Performance Rating of Unitary Air-Conditioning & Air-Source Heat Pump Equipment

Size: px
Start display at page:

Download "Performance Rating of Unitary Air-Conditioning & Air-Source Heat Pump Equipment"

Transcription

1 ANSI/AHRI Standard 210/240 with Addenda 1 and 2 (formerly ARI Standard 210/240) 2008 Standard for Performane Rating of Unitary Air-Conditioning & Air-Soure Heat Pump Equipment Approved by ANSI in Deember 2012

2 ANSI/AHRI STANDARD 210/ WITH ADDENDUM 2 Performane Rating of Unitary Air-Conditioning & Air-Soure Heat Pump Equipment Marh 2012 Addendum 2 of ANSI/AHRI Standard 210/ , is provided as follows. The following hanges have been inorporated (additions are shown with highlights; deletions are shown by strikethroughs) into the already published 2008 version of ANSI/AHRI Standard 210/240 with Addendum 1 to avoid onfusion: The Integrated Energy Effiieny Ratio (IEER) methodology has been added to the standard for water-ooled and evaporatively-ooled produts. It is not intended for air-ooled produts whih should be rated with SEER. This inludes: 1. The addition of definition of IEER (page 2) 2. The addition of and in multiples of 0.1 for IEER to Setion (page 5). 3. The addition of Part-Load IEER Conditions to Test Conditions to Table 12 (page 21) 4. The reinstatement of Note 2 in Table 12 (page 21) 5. New Setion 6.2 Part Load Ratings (pages 22-26). This new Setion 6.2 is dupliated from Setion 6.2 from AHRI Standard 340/ with addenda 1 and The addition of plus the IEER (where appliable), to Setion 6.4 (page 26) 7. The addition of exept IEER whih shall not be less than 90% of Published Ratings. to Setion 6.5 (page 26) 8. The addition of 3. Integrated Energy Effiieny Ratio, IEER, to Setion 7.1.b (page 27) Prie $10.00 (M) $20.00 (NM) Printed in U.S.A. Copyright 2008, by Air-Conditioning, Heating, and Refrigeration Institute Registered United States Patent and Trademark Offie

3 ANSI/AHRI STANDARD 210/ WITH ADDENDUM 1 Performane Rating of Unitary Air-Conditioning & Air-Soure Heat Pump Equipment June 2011 Addendum 1 of ANSI/AHRI Standard 210/ , is provided as follows. The following hanges have been inorporated (deletions are shown by strikethroughs) into the already published 2008 version of ANSI/AHRI Standard 210/240 to avoid onfusion: The Integrated Part-Load Values (IPLV) methodology has been removed from the standard. This inludes the deletion of: 9. Setion 3.6 Integrated Part Load Value (IPLV) Definition (page 2) 10. and in multiples of 0.1 for IPLV from Setion (page 5) 11. The Part Load Conditions line and Note 2 of Table 12 (page 21) 12. Setion 6.2 Part Load Ratings (pages 21-22) 13. plus the IPLV (where appliable) from Setion 6.4 (page 22) 14. Appendix E. The orresponding Table E1 has also been removed (pages )

4 IMPORTANT SAFETY DISCLAIMER AHRI does not set safety standards and does not ertify or guarantee the safety of any produts, omponents or systems designed, tested, rated, installed or operated in aordane with this standard/guideline. It is strongly reommended that produts be designed, onstruted, assembled, installed and operated in aordane with nationally reognized safety standards and ode requirements appropriate for produts overed by this standard/guideline. AHRI uses its best efforts to develop standards/guidelines employing state-of-the-art and aepted industry praties. AHRI does not ertify or guarantee that any tests onduted under its standards/guidelines will be non-hazardous or free from risk. AHRI CERTIFICATION PROGRAM PROVISIONS Sope of the Certifiation Program The Certifiation Program inludes all Unitary Air-Conditioning and Air-Soure Unitary Heat Pump equipment rated below 65,000 Btu/h [19,000 W] at AHRI Standard Rating Conditions (Cooling). Certified Ratings The following Certifiation Program ratings are verified by test: Unitary Air-Conditioners A. Air-ooled under 65,000 Btu/h [19,000 W] 1. AHRI Standard Rating Cooling Capaity, Btu/h [W] 2. Seasonal Energy Effiieny Ratio, SEER, Btu/(W h) B. Water-ooled and evaporatively-ooled under 65,000 Btu/h [19,000 W] 1. AHRI Standard Rating Cooling Capaity, Btu/h [W] 2. Energy Effiieny Ratio, EER, Btu/(W h) 3. Integrated Energy Effiieny Ratio, IEER, Btu/(W h) Air-Soure Unitary Heat Pumps Air-ooled under 65,000 Btu/h [19,000 W] 1. AHRI Standard Rating Cooling Capaity, Btu/h [W] 2. Seasonal Energy Effiieny Ratio, SEER, Btu/(W h) 3. High Temperature Heating Standard Rating Capaity, Btu/h [W] 4. Region IV Heating Seasonal Performane Fator, HSPF, Minimum Design Heating Requirement, Btu/(W h) Conformane to the requirements of the Maximum Operating Conditions Test, Voltage Tolerane Test, Low- Temperature Operation Test (Cooling), Insulation Effetiveness Test (Cooling), and Condensate Disposal Test (Cooling), as outlined in Setion 8, are also verified by test. Note: This standard supersedes ARI Standard 210/ Prie $10.00 (M) $20.00 (NM) Printed in U.S.A. Copyright 2008, by Air-Conditioning, Heating, and Refrigeration Institute Registered United States Patent and Trademark Offie

5 TABLE OF CONTENTS SECTION PAGE Setion 1. Purpose... 1 Setion 2. Sope... 1 Setion 3. Definitions... 1 Setion 4. Classifiations... 4 Setion 5. Test Requirements... 4 Setion 6. Rating Requirements... 4 Setion 7. Minimum Data Requirements for Published Ratings Setion 8. Operating Requirements Setion 9. Marking and Nameplate Data Setion 10. Conformane Conditions TABLES Table 1. Classifiation of Unitary Air-Conditioners... 6 Table 2. Classifiation of Air-Soure Unitary Heat Pumps... 7 Table 3. Table 4. Table 5. Table 6. Cooling Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed-Speed Indoor Fan, a Constant Air Volume Rate Indoor Fan, or No Indoor Fan Heating Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed-Speed Indoor Fan, a Constant Air Volume Rate Indoor Fan, or No Indoor Fan Cooling Mode Test Conditions for Units Having a Single-Speed Compressor and a Variable Air Volume Rate Indoor Fan that Correlates with the Outdoor Dry Bulb Temperature (Setion ) Heating Mode Test Conditions for Units Having a Single-Speed Compressor and a Variable Air Volume Rate Indoor Fan... 16

6 TABLES (Cont d) Table 7. Table 8. Table 9. Table 10. Table 11. Table 12. Cooling Mode Test Conditions for Units Having a Two-Capaity Compressor Heating Mode Test Conditions for Units Having a Two-Capaity Compressor Cooling Mode Test Conditions for Units Having a Variable-Speed Compressor Heating Mode Test Conditions for Units Having a Variable-Speed Compressor Minimum External Stati Pressure for Duted Systems Tested with an Indoor Fan Installed Conditions for Standard Rating Tests and Operating Requirement Tests for Water-ooled and Evaporatively-ooled Equipment Using ASHRAE Standard Table 12A. IEER Part-Load Rating Conditions Table 13. Conditions for Operating Requirement Tests for Air-ooled Equipment FIGURE Figure 1. Part-Load Fator Curve APPENDICES Appendix A. Referenes Normative Appendix B. Referenes Informative Appendix C. Uniform Test Method for Measuring the Energy Consumption of Central Air Conditioners and Heat Pumps Normative Appendix D. Presriptive Methodology for the Cyli Testing of Duted Systems Normative Appendix E. Example of Calulating Integrated Part-Load Values (IPLV) Normative

7 TABLE FOR APPENDICES Table E1. Example IPLV Calulation FIGURES FOR APPENDICES Figure D1. Tunnel Air Enthalpy Test Method Arrangement Figure D2. Loop Air Enthalpy Test Method Arrangement Figure D3. Calorimeter Air Enthalpy Test Method Arrangement Figure D4. Room Air Enthalpy Test Method Arrangement

8 ANSI/AHRI STANDARD 210/ PERFORMANCE RATING OF UNITARY AIR- CONDITIONING AND AIR-SOURCE HEAT PUMP EQUIPMENT Setion 1. Purpose 1.1 Purpose. The purpose of this standard is to establish, for Unitary Air-Conditioners and Air-Soure Unitary Heat Pumps: definitions; lassifiations; test requirements; rating requirements; minimum data requirements for Published Ratings; operating requirements; marking and nameplate data; and onformane onditions Intent. This standard is intended for the guidane of the industry, inluding manufaturers, engineers, installers, ontrators and users Review and Amendment. This standard is subjet to review and amendment as tehnology advanes. Setion 2. Sope 2.1 Sope. This standard applies to fatory-made Unitary Air-Conditioners and Air-Soure Unitary Heat Pumps as defined in Setion Energy Soure. This standard applies only to eletrially operated, vapor ompression refrigeration systems. 2.2 Exlusions This standard does not apply to the rating and testing of individual assemblies, suh as ondensing units or oils, for separate use This standard does not apply to heat operated air-onditioning/heat pump equipment, or to pakaged terminal air-onditioners/heat pumps, or to room air-onditioners/heat pumps This standard does not apply to Unitary Air-Conditioners as defined in AHRI Standard 340/360 with apaities of 65,000 Btu/h [19,000 W] or greater This standard does not apply to Air-Soure Unitary Heat Pumps as defined in AHRI Standard 340/360 with ooling apaities of 65,000 Btu/h [19,000 W] or greater, or to water-soure heat pumps, to ground water-soure heat pumps, and to ground soure losed-loop heat pumps This standard does not inlude water heating heat pumps This standard does not apply to rating units equipped with desuperheater/water heating devies in operation. Setion 3. Definitions All terms in this doument shall follow the standard industry definitions in the urrent edition of ASHRAE Terminology of Heating, Ventilation, Air- Conditioning and Refrigeration, unless otherwise defined in this setion. Note: Definitions for Small-dut, High-veloity Systems, Spae Constrained Produts, and Through-the-wall Air Conditioners and Heat Pumps are taken from Title 10, Code of Federal Regulations, Part 430, Subparts and (). See Appendix C for definitions that apply to the testing and alulation proedures required by Appendix C. 1

9 ANSI/AHRI STANDARD 210/ Air-Soure Unitary Heat Pump. One or more fatory-made assemblies whih normally inlude an indoor onditioning oil(s), ompressor(s), and outdoor oil(s), inluding means to provide a heating funtion. When suh equipment is provided in more than one assembly, the separated assemblies shall be designed to be used together, and the requirements of rating outlined in the standard are based upon the use of mathed assemblies Funtions. They shall provide the funtion of air heating with ontrolled temperature, and may inlude the funtions of air-ooling, air-irulating, air-leaning, dehumidifying or humidifying. 3.2 Degradation Coeffiient (C D ). The measure of the effiieny loss due to the yling of the units as determined in Appendies C and D. 3.3 Design Heating Requirement (DHR). This is the amount of heating required to maintain a given indoor temperature at a partiular outdoor design temperature. 3.4 Energy Effiieny Ratio (EER). A ratio of the ooling apaity in Btu/h to the power input value in watts at any given set of Rating Conditions expressed in Btu/(W h) Standard Energy Effiieny Ratio. A ratio of the apaity to power input value obtained at Standard Rating Conditions Integrated Energy Effiieny Ratio (IEER). A single number ooling part-load effiieny figure of merit alulated per the method desribed in Setion expressed in Btu/(W h). 3.5 Heating Seasonal Performane Fator (HSPF). The total spae heating required during the spae heating season, expressed in Btu s, divided by the total eletrial energy onsumed by the heat pump system during the same season, expressed in watt-hours. 3.6 Integrated Part-Load Value (IPLV). A single number part-load effiieny figure of merit alulated per the method desribed in this standard. 3.7 Published Rating. A statement of the assigned values of those performane harateristis, under stated Rating Conditions, by whih a unit may be hosen to fit its appliation. These values apply to all units of like nominal apaity and type (identifiation) produed by the same manufaturer. As used herein, the term Published Rating inludes the rating of all performane harateristis shown on the unit or published in speifiations, advertising, or other literature ontrolled by the manufaturer, at stated Rating Conditions Appliation Rating. A rating based on tests performed at Appliation Rating Conditions (other than Standard Rating Conditions) Standard Rating. A rating based on tests performed at Standard Rating Conditions. 3.8 Rating Conditions. Any set of operating onditions under whih a single level of performane results and whih auses only that level of performane to our Standard Rating Conditions. Rating Conditions used as the basis of omparison for performane harateristis. 3.9 Seasonal Energy Effiieny Ratio (SEER). The total heat removed from the onditioned spae during the annual ooling season, expressed in Btu s, divided by the total eletrial energy onsumed by the air onditioner or heat pump during the same season, expressed in watt-hours "Shall" or "Should". "Shall" or "should" shall be interpreted as follows: Shall. Where "shall" or "shall not" is used for a provision speified, that provision is mandatory if ompliane with the standard is laimed Should. "Should" is used to indiate provisions whih are not mandatory but whih are desirable as good pratie. 2

10 ANSI/AHRI STANDARD 210/ Small-dut, High-veloity System. A heating and/or ooling produt that ontains a blower and indoor oil ombination that is designed for, and produes, at least 1.2 in H 2 O [300 Pa] of external stati pressure when operated at the ertified air volume rate of fm [ m 3 /s] per rated ton [12,000 Btu/h] of ooling. When applied in the field, small-dut produts use high-veloity room outlets (i.e., generally greater than 1,000 fpm [5 m/s]) having less than 6.0 in 2 [3,900 mm 2 ] of free area Spae Constrained Produt. A entral air onditioner or heat pump: a. that has rated ooling apaities no greater than 30,000 Btu/h [8,800 W]; b. that has an outdoor or indoor unit having at least two overall exterior dimensions or an overall displaement that: 1. is substantially smaller than those of other units that are: a. urrently usually installed in site built single family homes; and b. of a similar ooling, and, if a heat pump, heating apaity; and 2. if inreased, would ertainly result in a onsiderable inrease in the usual ost of installation or would ertainly result in a signifiant loss in the utility of the produt to the onsumer; and. of a produt type that was available for purhase in the United States as of Deember 1, Standard Air. Air weighing lb/ft 3 [1.2 kg/m 3 ] whih approximates dry air at 70 F [21 C] and at a barometri pressure of in Hg [101.3 kpa] Tested Combination for Multiple-split air onditioners and heat pumps Tested ombination means a multi-split system with multiple indoor oils having the following features: The basi model of a system used as a tested ombination shall onsist of one outdoor unit, with one or more ompressors, that is mathed with between 2 and 5 indoor units; for multi-split systems, eah of these indoor units shall be designed for individual operation The indoor units shall: Represent the highest sales model family, or another indoor model family if the highest sales model family does not provide suffiient apaity (see ); Together, have a nominal ooling apaity that is between 95% and 105% of the nominal ooling apaity of the outdoor unit; Not, individually, have a apaity that is greater than 50% of the nominal apaity of the outdoor unit; Operate at fan speeds that are onsistent with the manufaturer's speifiations; and All be subjet to the same minimum external stati pressure requirement (i.e., 0 in H 2 O [0 Pa]) for non-duted, see Table 2 in Appendix M to Subpart B of this part for duted indoor units) while being onfigurable to produe the same stati pressure at the exit of eah outlet plenum when manifolded as per setion of Appendix M to Subpart B of Part 430 Uniform Test Method for Measuring the Energy Consumption of Central Air Conditioners and Heat Pumps Through-the-wall Air Conditioner and Heat Pump. A entral air onditioner or heat pump that is designed to be installed totally or partially within a fixed-size opening in an exterior wall, and: a. is manufatured prior to January 23, 2010; b. is not weatherized;. is learly and permanently marked for installation only through an exterior wall; d. has a rated ooling apaity no greater than 30,000 Btu/h [8,800 W]; e. exhanges all of its outdoor air aross a single surfae of the equipment abinet; and f. has a ombined outdoor air exhange area of less than 800 in 2 [0.516 m 2 ] (split systems) or less than 1,210 in 2 [ m 2 ] (single pakaged systems) as measured on the surfae desribed in 3.14.e. 3

11 ANSI/AHRI STANDARD 210/ Two-apaity (or Two-stage) Compressor. An air onditioner or heat pump that has one of the following: a. A two-speed ompressor, b. Two ompressors where only one ompressor ever operates at a time,. Two ompressors where one ompressor (Compressor #1) operates at low loads and both ompressors (Compressors #1 and #2) operate at high loads but Compressor #2 never operates alone, or d. A ompressor that is apable of ylinder or sroll unloading. For suh systems, low apaity means: a. Operating at low ompressor speed, b. Operating the lower apaity ompressor,. Operating Compressor #1, or d. Operating with the ompressor unloading (e.g., operating one piston of a two-piston reiproating ompressor, using a fixed frational volume of the full sroll, et.). For suh systems, high apaity means: a. Operating at high ompressor speed, b. Operating the higher apaity ompressor,. Operating Compressors #1 and #2, or d. Operating with the ompressor loaded (e.g., operating both pistons of a two-piston reiproating ompressor, using the full volume of the sroll) Unitary Air-Conditioner. One or more fatory-made assemblies whih normally inlude an evaporator or ooling oil(s), ompressor(s), and ondenser(s). Where suh equipment is provided in more than one assembly, the separated assemblies are to be designed to be used together, and the requirements of rating outlined in this standard are based upon the use of these assemblies in operation together Funtions. Either alone or in ombination with a heating plant, the funtions are to provide air-irulation, air leaning, ooling with ontrolled temperature and dehumidifiation, and may optionally inlude the funtion of heating and/or humidifying. Setion 4. Classifiations Equipment overed within the sope of this standard shall be lassified as shown in Tables 1 and 2. Setion 5. Test Requirements All Standard Ratings shall be verified by tests onduted in aordane with the test methods and proedures as desribed in this standard and its appendies. Air-ooled units shall be tested in aordane with ANSI/ASHRAE Standard 37 and with Appendies C and D. Water-ooled and evaporatively-ooled units shall be tested in aordane with ANSI/ASHRAE Standard 37. Setion 6. Rating Requirements 6.1 Standard Ratings. Standard Ratings shall be established at the Standard Rating Conditions speified in Air-ooled units shall be rated at onditions speified in Tables Water-ooled and evaporatively-ooled units shall be rated at onditions speified in Table 12. Standard Ratings relating to ooling or heating apaities shall be net values, inluding the effets of irulating-fan heat, but not inluding supplementary heat. Power input shall be the total power input to the ompressor(s) and fan(s), plus ontrols and other items required as part of the system for normal operation. Standard Ratings of units whih do not have indoor air-irulating fans furnished as part of the model, i.e., split systems with indoor oil alone, shall be established by subtrating from the total ooling apaity 1,250 Btu/h per 1,000 fm [775 W/m 3 /s], and by adding the same 4

12 ANSI/AHRI STANDARD 210/ amount to the heating apaity. Total power input for both heating and ooling shall be inreased by 365 W per 1,000 fm [226 W/m 3 /s] of indoor air irulated. Standard Ratings of water-ooled units shall inlude a total allowane for ooling tower fan motor and irulating water pump motor power inputs to be added in the amount of 10.0 W per 1,000 Btu/h [34.1 W per 1,000 W] ooling apaity Values of Standard Capaity Ratings. These ratings shall be expressed only in terms of Btu/h [W] as shown: Capaity Ratings, Multiples, Btu/h [W] Btu/h [W] < 20,000 [5,900] 100 [30] 20,000 and < 38,000 [5,900 up to 11,000] 200 [60] 38,000 and < 65, [150] [11,000 up to 19,000] Values of Measures of Energy Effiieny. Standard measures of energy effiieny, whenever published, shall be expressed in multiples of the nearest 0.05 Btu/(W h) for EER, SEER and HSPF, and in multiples of 0.1 for IEER. and in multiples of 0.1 for IPLV Standard Rating Tests. Tables 3-10 and 12 indiate the test and test onditions whih are required to determine values of standard apaity ratings and values of measures of energy effiieny. 5

13 ANSI/AHRI STANDARD 210/ Table 1. Classifiation of Unitary Air-Conditioners Types of Unitary Air-Conditioners Designation AHRI Type 1,2 Arrangement Single Pakage SP-A SP-E SP-W FAN EVAP COMP COND Year-Round Single Pakage SPY-A SPY-E SPY-W FAN HEAT EVAP COMP COND Remote Condenser RC-A RC-E RC-W FAN EVAP COND Year-Round Remote Condenser RCY-A RCY-E RCY-W FAN EVAP HEAT COND Condensing Unit, Coil Alone RCU-A-C RCU-E-C RCU-W-C EVAP COND COMP Condensing Unit, Coil And Blower RCU-A-CB RCU-E-CB RCU-W-CB FAN EVAP COND COMP Year-Round Condensing Unit, Coil and Blower Through-the-wall Air Conditioner Spae Constrained Produts Small-dut, High-veloity System Notes: RCUY-A-CB RCUY-E-CB RCUY-W-CB TTW-SP-A,E,W TTW-SPY-A,E,W TTW-RCU-A,E,W-C TTW-RCU-A,E,W-CB TTW-RCUY-A,E,W-CB SCP-SP-A,E,W SCP-SPY-A,E,W SCP-RCU-A,E,W-C SCP-RCU-A,E,W-CB SCP-RCUY-A,E,W-CB SDHV-SP-A,E,W SDHV-SPY-A,E,W SDHV-RCU-A,E,W-C SDHV-RCU-A,E,W-CB SDHV-RCUY-A,E,W-CB FAN EVAP COND HEAT COMP FAN COMP EVAP COND or FAN COMP EVAP COND or FAN COMP EVAP COND or FAN EVAP FAN EVAP FAN EVAP COND COMP COND COMP COND COMP 1 2 A suffix of "-O" following any of the above lassifiations indiates equipment not intended for use with field-installed dut systems ( ). A suffix of "-A" indiates air-ooled ondenser, "-E" indiates evaporatively-ooled ondenser and "-W" indiates water-ooled ondenser. 6

14 ANSI/AHRI STANDARD 210/ Table 2. Classifiation of Air-Soure Unitary Heat Pumps Types of Air-Soure Unitary Heat Pumps Designation AHRI Type 1 Arrangement Heating and Cooling Heating Only Single Pakage HSP-A HOSP-A FAN INDOOR COIL COMP OUTDOOR COIL Remote Outdoor Coil HRC-A-CB HORC-A-CB FAN INDOOR COIL COMP OUTDOOR COIL Remote Outdoor Coil With No Indoor Fan HRC-A-C HORC-A-C INDOOR COIL COMP OUTDOOR COIL Split System HRCU-A-CB HORCU-A-CB FAN COMP INDOOR COIL OUTDOOR COIL Split System With No Indoor Fan HRCU-A-C HORCU-A-C COMP INDOOR COIL OUTDOOR COIL Through-the-wall Heat Pump TTW-HSP-A TTW-HRCU-A-C TTW-HRCU-A-CB TTW-HOSP-A TTW-HORCU-A-C TTW-HORCU-A-CB FAN INDOOR COIL COMP OUTDOOR COIL or FAN INDOOR COIL COMP OUTDOOR COIL Spae Constrained Produts SCP-HSP-A SCP-HRCU-A-C SCP-HRCU-A-CB SCP-HOSP-A SCP-HORCU-A-C SCP-HORCU-A-CB FAN INDOOR COIL COMP OUTDOOR COIL or FAN INDOOR COIL COMP OUTDOOR COIL Small-dut, Highveloity System SDHV-HSP-A SDHV-HRCU-A-C SDHV-HRCU-A-CB SDHV-HOSP-A SDHV-HORCU-A-C SDHV-HORCU-A-CB FAN INDOOR COIL COMP OUTDOOR COIL or FAN INDOOR COIL COMP OUTDOOR COIL Note: 1 A suffix of "-O" following any of the above lassifiations indiates equipment not intended for use with field-installed dut systems ( ) Assigned Degradation Fator. In lieu of onduting C and D tests or the heating yling test, an assigned value of 0.25 may be used for either the ooling or heating Degradation Coeffiient, C D, or both. For units with two ompressor speeds, two ompressors or ylinder unloading, if the assigned C D is used for one ooling mode, it must be used for both ooling modes. If the assigned C D is used for one heating mode, it must be used for both heating modes Eletrial Conditions. Standard Rating tests shall be performed at the nameplate rated voltage(s) and frequeny. For air-ooled equipment whih is rated with V dual nameplate voltages, Standard Rating tests shall be performed at 230 V. For all other dual nameplate voltage equipment overed by this standard, the Standard Rating tests shall be performed at both voltages or at the lower of the two voltages if only a single Standard Rating is to be published. 7

15 ANSI/AHRI STANDARD 210/ Airflow Through The Indoor Coil Cooling Full-load Air Volume Rate Cooling Full-load Air Volume Rate for Duted Units. The manufaturer must speify the Cooling Full-load Air Volume Rate. Use this value as long as the following two requirements are satisfied. First, when onduting the A or A 2 test (exlusively), the measured air volume rate, when divided by the measured indoor air-side total ooling apaity, must not exeed 37.5 sfm per 1,000 Btu/h [0.06 m 3 /s per 1,000 W]. If this ratio is exeeded, redue the air volume rate until this ratio is equaled. Use this redued air volume rate for all tests that all for using the Cooling Full-load Air Volume Rate. The seond requirement is as follows: a. For all duted units tested with an indoor fan installed, exept those having a variablespeed, onstant-air-volume-rate indoor fan. The seond requirement applies exlusively to the A or A 2 Test and is met as follows. 1. Ahieve the Cooling Full-load Air Volume Rate, determined in aordane with the previous paragraph; 2. Measure the external stati pressure; 3. If this pressure is equal to or greater than the appliable minimum external stati pressure ited in Table 11, this seond requirement is satisfied. Use the urrent air volume rate for all tests that require the Cooling Full-load Air Volume Rate. 4. If the Table 11 minimum is not equaled or exeeded, 4a. redue the air volume rate until the appliable Table 11 minimum is equaled or 4b. until the measured air volume rate equals 95 perent of the air volume rate from step 1, whihever ours first. 5. If the onditions of step 4a our first, this seond requirement is satisfied. Use the step 4a redued air volume rate for all tests that require the Cooling Full-load Air Volume Rate. 6. If the onditions of step 4b our first, make an inremental hange to the set-up of the indoor fan (e.g., next highest fan motor pin setting, next highest fan motor speed) and repeat the evaluation proess beginning at above step 1. If the indoor fan set-up annot be further hanged, redue the air volume rate until the appliable Table 11 minimum is equaled. Use this redued air volume rate for all tests that require the Cooling Full-load Air Volume Rate. b. For duted units that are tested with a variable-speed, onstant-air-volume-rate indoor fan installed. For all tests that speify the ooling full-load air volume rate, obtain an external stati pressure as lose to (but not less than) the appliable Table 11 value that does not ause instability or an automati shutdown of the indoor blower.. For duted units that are tested without an indoor fan installed. For the A or A 2 test, (exlusively), the pressure drop aross the indoor oil assembly must not exeed 0.30 in H 2 O [75 Pa]. If this pressure drop is exeeded, redue the air volume rate until the measured pressure drop equals the speified maximum. Use this redued air volume rate for all tests that require the ooling full-load air volume rate Cooling Full-load Air Volume Rate for Non-duted Units. For non-duted units, the ooling full-load air volume rate is the air volume rate that results during eah test when the unit is operated at an external stati pressure of zero in H 2 O [0 Pa]. 8

16 ANSI/AHRI STANDARD 210/ Cooling Minimum Air Volume Rate. a. For duted units that regulate the speed (as opposed to the fm) of the indoor fan, Cooling Minimum Air Vol. Rate = Cooling Minimum Fan Speed Cooling Full - load Air Vol. Rate A Test Fan Speed 2 where ooling minimum fan speed orresponds to the fan speed used when operating at low ompressor apaity (two-apaity system), the fan speed used when operating at the minimum ompressor speed (variable-speed system), or the lowest fan speed used when ooling (single-speed ompressor and a variable-speed variable-air-volume-rate indoor fan). For suh systems, obtain the ooling minimum air volume rate regardless of the external stati pressure. b. For duted units that regulate the air volume rate provided by the indoor fan, the manufaturer must speify the ooling minimum air volume rate. For suh systems, ondut all tests that speify the ooling minimum air volume rate (i.e., the A 1, B 1, C 1, F 1, and G 1 tests) at an external stati pressure that does not ause instability or an automati shutdown of the indoor blower while being as lose to, but not less than, A, B, C, F, and GΔPTest ΔP st st,a 2 Cooling Minimum Air Volume Rate = Cooling Full load Air Volume Rate 2 where ΔP is the appliable Table 11 minimum external stati pressure that was targeted during the A 2 st,a 2 (and B 2 ) test.. For duted two-apaity units that are tested without an indoor fan installed, the ooling minimum air volume rate is the higher of (1) the rate speified by the manufaturer or (2) 75 perent of the ooling fullload air volume rate. During the laboratory tests on a oil-only (fanless) unit, obtain this ooling minimum air volume rate regardless of the pressure drop aross the indoor oil assembly. d. For non-duted units, the ooling minimum air volume rate is the air volume rate that results during eah test when the unit operates at an external stati pressure of zero in H 2 O [0 Pa] and at the indoor fan setting used at low ompressor apaity (two-apaity system) or minimum ompressor speed (variable-speed system). For units having a single-speed ompressor and a variable-speed variable-air-volume-rate indoor fan, use the lowest fan setting allowed for ooling Cooling Intermediate Air Volume Rate. a. For duted units that regulate the speed of the indoor fan, E Test Fan Speed V Cooling Intermediate Air Volume Rate = Cooling Full load Air Volume Rate A Test Fan Speed For suh units, obtain the ooling intermediate air volume rate regardless of the external stati pressure. b. For duted units that regulate the air volume rate provided by the indoor fan, the manufaturer must speify the ooling intermediate air volume rate. For suh systems, ondut the E V test at an external stati pressure that does not ause instability or an automati shutdown of the indoor blower while being as lose to, but not less than, 2 E V Test ΔP st,a 2 Cooling Intermediate Air Volume Rate Cooling Full load Air Volume Rate 2 9

17 ANSI/AHRI STANDARD 210/ where ΔP is the appliable Table 11 minimum external stati pressure that was targeted during the A 2 st,a 2 (and B 2 ) test.. For non-duted units, the ooling intermediate air volume rate is the air volume rate that results when the unit operates at an external stati pressure of zero in H 2 O [0 Pa] and at the fan speed seleted by the ontrols of the unit for the E V test onditions Heating Full-load Air Volume Rate Duted Heat Pumps Where the Heating and Cooling Full-load Air Volume Rates Are the Same. a. Use the ooling full-load air volume rate as the heating full-load air volume rate for: 1. Duted heat pumps that operate at the same indoor fan speed during both the A (or A 2 ) and the H1 (or H1 2 ) tests; 2. Duted heat pumps that regulate fan speed to deliver the same onstant air volume rate during both the A (or A 2 ) and the H1 (or H1 2 ) tests; and 3. Duted heat pumps that are tested without an indoor fan installed (exept two-apaity northern heat pumps that are tested only at low apaity ooling - see ). b. For heat pumps that meet the above riteria 1 and 3, no minimum requirements apply to the measured external or internal, respetively, stati pressure. For heat pumps that meet the above riterion 2, test at an external stati pressure that does not ause instability or an automati shutdown of the indoor blower while being as lose to, but not less than, the same Table 11 minimum external stati pressure as was speified for the A (or A 2 ) ooling mode test Duted Heat Pumps Where the Heating and Cooling Full-load Air Volume Rates Are Different Due To Indoor Fan Operation. a. For duted heat pumps that regulate the speed (as opposed to the fm) of the indoor fan, Heating Full load Air Volume Rate = H1 or H1 Test Fan Speed 2 Cooling Full load Air Volume Rate A or A Test Fan Speed 2 For suh heat pumps, obtain the heating full-load air volume rate without regard to the external stati pressure. b. For duted heat pumps that regulate the air volume rate delivered by the indoor fan, the manufaturer must speify the heating full-load air volume rate. For suh heat pumps, ondut all tests that speify the heating full-load air volume rate at an external stati pressure that does not ause instability or an automati shutdown of the indoor blower while being as lose to, but not less than, Heating Air Volume Rate Heating Full load ΔP Cooling = Full Load ΔP st st Cooling Air Volume Rate 2 where the ooling full-load ΔP st,h1 2 is the appliable Table 11 pressure that was speified for the A or A 2 test. minimum external stati 10. When testing duted, two-apaity northern heat pumps (see Definition 1.46 of Appendix C), use the appropriate approah of the above two ases for units that are tested with an indoor fan installed. For oil-only (fanless) northern heat pumps, the heating full-load air volume rate is

18 ANSI/AHRI STANDARD 210/ the lesser of the rate speified by the manufaturer or 133 perent of the ooling full-load air volume rate. For this latter ase, obtain the heating full-load air volume rate regardless of the pressure drop aross the indoor oil assembly Duted Heating-Only Heat Pumps. The manufaturer must speify the heating full-load air volume rate. a. For all duted heating-only heat pumps tested with an indoor fan installed, exept those having a variable-speed, onstant-air-volume-rate indoor fan. Condut the following steps only during the first test, the H1 or H1 2 Test. 1. Ahieve the Heating Full-load Air Volume Rate. 2. Measure the external stati pressure. 3. If this pressure is equal to or greater than the Table 11 minimum external stati pressure that applies given the heating-only heat pump s rated heating apaity, use the urrent air volume rate for all tests that require the Heating Full-load Air Volume Rate. 4. If the Table 11 minimum is not equaled or exeeded, 4a. redue the air volume rate until the appliable Table11 minimum is equaled or 4b. until the measured air volume rate equals 95 perent of the manufaturer-speified Fullload Air Volume Rate, whihever ours first. 5. If the onditions of step 4a ours first, use the step 4a redued air volume rate for all tests that require the Heating Full-load Air Volume Rate. 6. If the onditions of step 4b our first, make an inremental hange to the set-up of the indoor fan (e.g., next highest fan motor pin setting, next highest fan motor speed) and repeat the evaluation proess beginning at above step 1. If the indoor fan set-up annot be further hanged, redue the air volume rate until the appliable Table 11 minimum is equaled. Use this redued air volume rate for all tests that require the Heating Full-load Air Volume Rate. b. For duted heating-only heat pumps that are tested with a variable-speed, onstant-air-volumerate indoor fan installed. For all tests that speify the heating full load air volume rate, obtain an external stati pressure that does not ause instability or an automati shutdown of the indoor blower while being as lose to, but not less than, the appliable Table 11 minimum.. For duted heating-only heat pumps that are tested without an indoor fan installed. For the H1 or H1 2 test, (exlusively), the pressure drop aross the indoor oil assembly must not exeed 0.30 in H 2 O [75 Pa]. If this pressure drop is exeeded, redue the air volume rate until the measured pressure drop equals the speified maximum. Use this redued air volume rate for all tests that require the heating full-load air volume rate Non-duted Heat Pumps, Inluding Non-duted Heating-only Heat Pumps. For non-duted heat pumps, the heating full-load air volume rate is the air volume rate that results during eah test when the unit operates at an external stati pressure of 0 in H 2 O [0 Pa] Heating Minimum Air Volume Rate. a. For duted heat pumps that regulate the speed (as opposed to the airflow) of the indoor fan, 11

19 ANSI/AHRI STANDARD 210/ Heating Minimum Air Volume Rate = Heating Minimum Fan Speed Heating Full load Air Volume Rate H1 Test Fan Speed 2 where heating minimum fan speed orresponds to the fan speed used when operating at low ompressor apaity (two-apaity system), the lowest fan speed used at any time when operating at the minimum ompressor speed (variable-speed system), or the lowest fan speed used when heating (single-speed ompressor and a variable-speed variable-air-volume-rate indoor fan). For suh heat pumps, obtain the heating minimum air volume rate without regard to the external stati pressure. b. For duted heat pumps that regulate the air volume rate delivered by the indoor fan, the manufaturer must speify the heating minimum air volume rate. For suh heat pumps, ondut all tests that speify the heating minimum air volume rate (i.e., the H0 1, H1 1, H2 1, and H3 1 tests) at an external stati pressure that does not ause instability or an automati shutdown of the indoor blower while being as lose to, but not less than, Heating Minimum Air Volume Rate H0,H1,H2,H3 Test P st,h1 2 Heating Full load Air Volume Rate 2 where ΔP is the minimum external stati pressure that was targeted during the H1 2 test. st,h1 2. For duted two-apaity northern heat pumps that are tested with an indoor fan installed, use the appropriate approah of the above two ases. d. For duted two-apaity heat pumps that are tested without an indoor fan installed, use the ooling minimum air volume rate as the heating minimum air volume rate. For duted twoapaity northern heat pumps that are tested without an indoor fan installed, use the ooling fullload air volume rate as the heating minimum air volume rate. For duted two-apaity heatingonly heat pumps that are tested without an indoor fan installed, the heating minimum air volume rate is the higher of the rate speified by the manufaturer or 75 perent of the heating full-load air volume rate. During the laboratory tests on a oil-only (fanless) unit, obtain the heating minimum air volume rate without regard to the pressure drop aross the indoor oil assembly. e. For non-duted heat pumps, the heating minimum air volume rate is the air volume rate that results during eah test when the unit operates at an external stati pressure of 0 in H 2 O [0 Pa] and at the indoor fan setting used at low ompressor apaity (two-apaity system) or minimum ompressor speed (variable-speed system). For units having a single-speed ompressor and a variable-speed, variable-air-volume-rate indoor fan, use the lowest fan setting allowed for heating Heating Intermediate Air Volume Rate. a. For duted heat pumps that regulate the speed of the indoor fan, Heating Intermediate Air Volume Rate = Heating Full load H2 Test Fan Speed V Air Volume Rate H1 Test Fan Speed 2 For suh heat pumps, obtain the heating intermediate air volume rate without regard to the external stati pressure. 12 b. For duted heat pumps that regulate the air volume rate delivered by the indoor fan, the manufaturer must speify the heating intermediate air volume rate. For suh heat pumps, ondut the H2 V test at an external stati pressure that does not ause instability or an automati

20 ANSI/AHRI STANDARD 210/ shutdown of the indoor blower while being as lose to, but not less than, H2 V Test ΔP = st, H1 2 Heating Intermediate Air Volume Rate Heating Full load Air Volume Rate 2 where ΔP is the minimum external stati pressure that was speified for the H1 2 test. st, H1 2. For non-duted heat pumps, the heating intermediate air volume rate is the air volume rate that results when the heat pump operates at an external stati pressure of zero in H 2 O [0 Pa] and at the fan speed seleted by the ontrols of the unit for the H2 V test onditions Heating Nominal Air Volume Rate. Exept for the noted hanges, determine the heating nominal air volume rate using the approah desribed in setion Required hanges inlude substituting H1 N test for H2 V test within the first setion equation, substituting H1 N test ΔP st for H2 V test ΔP st in the seond setion equation, substituting H1 N test for eah H2 V test, and substituting heating nominal air volume rate for eah heating intermediate air volume rate. Heating Nominal Air Volume Rate = H1 Test Fan Speed N Heating Air Volume Rate H1 Test Fan Speed 2 H1 Test ΔP = ΔP N st st,h1 2 Heating Nominal Air Volume Rate Heating Full load Air Volume Rate Outdoor-Coil Airflow Rate. All Standard Ratings shall be determined at the outdoor-oil airflow rate speified by the manufaturer where the fan drive is adjustable. Where the fan drive is non-adjustable, they shall be determined at the outdoor-oil airflow rate inherent in the equipment when operated with all of the resistane elements assoiated with inlets, louvers, and any dutwork and attahments onsidered by the manufaturer as normal installation pratie. One established, the outdoor oil air iruit of the equipment shall remain unhanged throughout all tests presribed herein Requirements For Separated Assemblies. All Standard Ratings for equipment in whih the outdoor setion is separated from the indoor setion, as in Types RC, RCY, RCU, RCUY, HRC, HORC, HRCU and HORCU (shown in Setion 4), shall be determined with at least 25 ft [7.6 m] of interonnetion tubing on eah line of the size reommended by the manufaturer. Suh equipment in whih the interonnetion tubing is furnished as an integral part of the mahine not reommended for utting to length shall be tested with the omplete length of tubing furnished, or with 25 ft [7.6 m] of tubing, whihever is greater. At least 10 ft [3.0 m] of the interonnetion tubing shall be exposed to the outside onditions. The line sizes, insulation, and details of installation shall be in aordane with the manufaturer s published reommendation Conditions For Standard Rating Tests Cooling Mode Tests For A Unit Having A Single-speed Compressor That Is Tested With A Fixedspeed Indoor Fan Installed, With A Constant-air-volume-rate Indoor Fan Installed, Or With No Indoor Fan Installed. Condut two steady-state wet oil tests, the A and B tests. Use the two optional dry-oil tests, the steady-state C test and the yli D test, to determine the ooling mode yli degradation oeffiient, C. If the two optional tests are not onduted, assign C the D D default value of Table 3 speifies test onditions for these four tests. 13

21 ANSI/AHRI STANDARD 210/ Table 3. Cooling Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed-Speed Indoor Fan, a Constant Air Volume Rate Indoor Fan, or No Indoor Fan Test Desription A Test required (steady, wet oil) B Test required (steady, wet oil) C Test optional (steady, dry oil) D Test optional (yli, dry oil) Notes: Air Entering Indoor Unit Temperature Dry-Bulb Wet-Bulb F C F C Air Entering Outdoor Unit Temperature Dry-Bulb Wet-Bulb F C F C Cooling Air Volume Rate (1) 23.9 (1) Cooling Fullload (2) (1) 18.3 (1) Cooling Fullload (2) (3) (3) Cooling Fullload (2) (4) (1) (2) (3) (4) The speified test ondition only applies if the unit rejets ondensate to the outdoor oil. Defined in setion The entering air must have a low enough moisture ontent so no ondensate forms on the indoor oil. (It is reommended that an indoor wet-bulb temperature of 57.0 F [13.9 C] or less be used.) Maintain the airflow nozzles stati pressure differene or veloity pressure during the ON period at the same pressure differene or veloity pressure as measured during the C Test Heating Mode Tests For A Heat Pump Having A Single-speed Compressor That Is Tested With A Fixed Speed Indoor Fan Installed, With A Constant-air-volume-rate Indoor Fan Installed, Or With No Indoor Fan Installed. Condut three tests: the high temperature (H1) test, the frost aumulation (H2) test, and the low temperature (H3) test. Condut the optional high temperature yli (H1C) test to determine h h the heating mode yli degradation oeffiient, C. If this optional test is not onduted, assign C the D D default value of Test onditions for these four tests are speified in Table 4. Table 4. Heating Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed-Speed Indoor Fan, a Constant Air Volume Rate Indoor Fan, or No Indoor Fan Test Desription H1 Test (required, steady) H1C Test (optional, yli) H2 Test (required) H3 Test (required, steady) Notes: Air Entering Indoor Unit Temperature Dry-Bulb Wet-Bulb F C F C Air Entering Outdoor Unit Temperature Dry-Bulb Wet-Bulb F C F C (max) 15.6 (max) (max) 15.6 (max) (max) 15.6 (max) (max) 15.6 (max) Heating Air Volume Rate Heating Fullload (1) (2) Heating Fullload (1) Heating Fullload (1) (1) (2) Defined in setion Maintain the airflow nozzles stati pressure differene or veloity pressure during the ON period at the same pressure differene or veloity pressure as measured during the H1 Test. 14

22 ANSI/AHRI STANDARD 210/ Cooling Mode Tests For A Unit Having A Single-speed Compressor And A Variable-speed Variable-air-volume-rate Indoor Fan Installed Indoor Fan Capaity Modulation That Correlates With The Outdoor Dry Bulb Temperature. Condut four steady-state wet oil tests: the A 2, A 1, B 2, and B 1 tests. Use the two optional dry-oil tests, the steady-state C 1 test and the yli D 1 test, to determine the ooling mode yli degradation oeffiient, C. If the two optional tests are not onduted, assign C the default value of Table 5 speifies test onditions for these six tests. D Indoor Fan Capaity Modulation Based On Adjusting The Sensible To Total (S/T) Cooling Capaity Ratio. The testing requirements are the same as speified in setion and Table 3. Use a ooling air volume rate that represents a normal residential installation. If performed, ondut the steady-state C test and the yli D test with the unit operating in the same S/T apaity ontrol mode as used for the B test. D Table 5. Cooling Mode Test Conditions for Units Having a Single-Speed Compressor and a Variable Air Volume Rate Indoor Fan that Correlates with the Outdoor Dry Bulb Temperature (Setion ) Test Desription A 2 Test - required (steady, wet oil) A 1 Test - required (steady, wet oil) B 2 Test - required (steady, wet oil) B 1 Test - required (steady, wet oil) C 1 Test (4) - optional (steady, dry oil) D 1 Test (4) - optional (yli, dry oil) Notes: Air Entering Indoor Unit Temperature Air Entering Outdoor Unit Temperature Cooling Air Dry-Bulb Wet-Bulb Dry-Bulb Wet-Bulb Volume Rate F C F C F C F C (1) 23.9 (1) Cooling Fullload (1) 23.9 (1) Cooling Minimum (3) (1) 18.3 (1) Cooling Fullload (2) (1) 18.3 (1) Cooling Minimum (3) (4) Cooling Minimum (3) (4) (5) (1) (2) (3) (4) (5) The speified test ondition only applies if the unit rejets ondensate to the outdoor oil. Defined in setion Defined in setion The entering air must have a low enough moisture ontent so no ondensate forms on the indoor oil. (It is reommended that an indoor wet-bulb temperature of 57.0 F [13.9 C] or less be used.) Maintain the airflow nozzles stati pressure differene or veloity pressure during the ON period at the same pressure differene or veloity pressure as measured during the C 1 Test Heating Mode Tests For A Heat Pump Having A Single-speed Compressor And A Variable-speed, Variable-air-volume-rate Indoor Fan: Capaity Modulation Correlates With Outdoor Dry Bulb Temperature. Condut five tests: two high temperature tests (H1 2 and H1 1 ), one frost aumulation test (H2 2 ), and two low temperature tests (H3 2 and H3 1 ). Conduting an additional frost aumulation test (H2 1 ) is optional. Condut the optional high temperature yli (H1C 1 ) test to determine the heating mode h h yli degradation oeffiient, C. If this optional test is not onduted, assign C the default value of D Table 6 speifies test onditions for these seven tests. If the optional H2 1 test is not done, use the equations in setion of Appendix C to approximate the apaity and eletrial power of the heat pump at the H2 1 test onditions: D 15

23 ANSI/AHRI STANDARD 210/ Test Desription H1 2 Test (required, steady) H1 1 Test (required, steady) H1C 1 Test (optional, yli) H2 2 Test (required) H2 1 Test (optional) H3 2 Test (required, steady) H3 1 Test (required, steady) Notes: Table 6. Heating Mode Test Conditions for Units Having a Single-Speed Compressor and a Variable Air Volume Rate Indoor Fan Air Entering Indoor Unit Temperature Dry-Bulb Wet-Bulb F C F C Air Entering Outdoor Unit Temperature Dry-Bulb Wet-Bulb F C F C (max) 15.6 (max) (max) 15.6 (max) (max) 15.6 (max) (max) 15.6 (max) (max) 15.6 (max) (max) 15.6 (max) (max) 15.6 (max) Heating Air Volume Rate Heating Fullload (1) Heating Minimum (2) (3) Heating Fullload (1) Heating Minimum (2) Heating Fullload (1) Heating Minimum (2) (1) (2) (3) Defined in setion Defined in setion Maintain the airflow nozzles stati pressure differene or veloity pressure during the ON period at the same pressure differene or veloity pressure as measured during the H1 1 Test Cooling Mode Tests For A Unit Having A Two-apaity Compressor. (See Definition 1.45 in Appendix C.) a. Condut four steady-state wet oil tests: the A 2, F 1, B 2, and B 1 tests. Use the two optional dry-oil tests, the steady-state C 1 test and the yli D 1 test, to determine the ooling mode yli degradation oeffiient, C. If the two optional tests are not onduted, assign C the default value of Table 7 speifies test onditions for these six tests. D b. For units having a variable speed indoor fan that is modulated to adjust the sensible to total (S/T) ooling apaity ratio, use ooling and ooling minimum air volume rates that represent a normal residential installation. Additionally, if onduting the optional dryoil tests, operate the unit in the same S/T apaity ontrol mode as used for the B 1 test.. Test two-apaity, northern heat pumps (see Definition 1.46 of Appendix C) in the same way as a single speed heat pump with the unit operating exlusively at low ompressor apaity (see setion and Table 3). d. If a two-apaity air onditioner or heat pump loks out low apaity operation at outdoor temperatures that are less than 95.0 F [35.0 C], ondut the F 1 test using the outdoor temperature onditions listed for the F 1 test in Table 9 rather than using the outdoor temperature onditions listed in Table 7 for the F 1 test. D 16

24 ANSI/AHRI STANDARD 210/ Test Desription Table 7. Cooling Mode Test Conditions for Units Having a Two-Capaity Compressor Air Entering Indoor Unit Air Entering Outdoor Unit Temperature Temperature Compressor Dry-Bulb Wet-Bulb Dry-Bulb Wet-Bulb Capaity F C F C F C F C Cooling Air Volume Rate A 2 Test required (steady, wet oil) (1) 23.9 (1) High B 2 Test required (steady, wet oil) (1) 18.3 (1) High B 1 Test required (steady, wet oil) (1) 18.3 (1) Low C 2 Test optional (4) (steady, dry-oil) High D 2 Test optional (4) (5) High (yli, dry-oil) C 1 Test optional (4) (steady, dry-oil) Low D 1 Test optional (4) (6) Low (yli, dry-oil) F 1 Test required (steady, wet oil) (1) 11.9 (1) Low (1) The speified test ondition only applies if the unit rejets ondensate to the outdoor oil. (2) Defined in setion (3) Defined in setion (4) The entering air must have a low enough moisture ontent so no ondensate forms on the indoor oil. DOE reommends using an indoor air wet-bulb temperature of 57.0 F [13.9 C] or less. (5) Maintain the airflow nozzle(s) stati pressure differene or veloity pressure during the ON period at the same pressure or veloity as measured during the C 2 Test. (6) Maintain the airflow nozzle(s) stati pressure differene or veloity pressure during the ON period at the same pressure or veloity as measured during the C 1 Test. Cooling Full- Load 2) Cooling Full- Load 2) Cooling Minimum (3) Cooling Full- Load (2) Cooling Minimum (3) Cooling Minimum (3) Heating Mode Tests For A Heat Pump Having A Two-apaity Compressor (See Definition 1.45 of Appendix C), Inluding Two-apaity, Northern Heat Pumps (See Definition 1.46 of Appendix C). a. Condut one maximum temperature test (H0 1 ), two high temperature tests (H1 2 and H1 1 ), one frost aumulation test (H2 2 ), and one low temperature test (H3 2 ). Condut an additional frost aumulation test (H2 1 ) and low temperature test (H3 1 ) if both of the following onditions exist: 1. knowledge of the heat pump s apaity and eletrial power at low ompressor apaity for outdoor temperatures of 37.0 F [2.78 C] and less is needed to omplete the Appendix C setion seasonal performane alulations, and 2. the heat pump s ontrols allow low apaity operation at outdoor temperatures of 37.0 F [2.78 C] and less. 17

25 ANSI/AHRI STANDARD 210/ b. Condut the optional maximum temperature yli test (H0C 1 ) to determine the heating mode h yli degradation oeffiient, C. If this optional test is not onduted, assign C the default D value of Table 8 speifies test onditions for these eight tests. h D Table 8. Heating Mode Test Conditions for Units Having a Two-Capaity Compressor Air Entering Indoor Unit Air Entering Outdoor Unit Temperature Temperature Compressor Test Desription Capaity Dry-Bulb F C Wet-Bulb F C Dry-Bulb F C Wet-Bulb F C Heating Air Volume Rate H0 1 Test (max) 15.6 (max) Heating Low (required, steady) Minimum (1) H1 2 Test (max) 15.6 (max) Heating High (required, steady) Full-Load (2) H1C 2 Test (max) 15.6 (max) (3) High (optional, yli) H1 1 Test (max) 15.6 (max) Heating Low (required) Minimum (1) H1C 1 Test (max) 15.6 (max) (4) Low (optional, yli) H2 2 Test (max) 15.6 (max) Heating Full High (required) Load (2) H2 1 Test (5,6) (max) 15.6 (max) Heating Low (required) Minimum (1) H3 2 Test (max) 15.6 (max) Heating Full High (required, steady) Load (2) H3 1 Test (5) (max) 15.6 (max) Heating Low (required, steady) Minimum (1) Defined in setion (2) Defined in setion (3) Maintain the airflow nozzle(s) stati pressure differene or veloity pressure during the ON period at the same pressure or veloity as measured during the H1 2 Test. (4) Maintain the airflow nozzle(s) stati pressure differene or veloity pressure during the ON period at the same pressure or veloity as measured during the H1 1 Test. (5) Required only if the heat pump s performane when operating at low ompressor apaity and outdoor temperatures less than 37.0 F [2.78 C] is needed to omplete the Appendix C setion HSPF alulations. (6) If table note #5 applies, the Appendix C setion equations for Q k = 1 h (35) and E k =1 h (35) may be used in lieu of onduting the H2 1 Test. 18

26 ANSI/AHRI STANDARD 210/ Tests For A Unit Having A Variable-speed Compressor. a. Condut five steady-state wet oil tests: the A 2, E V, B 2, B 1, and F 1 tests. Use the two optional dry-oil tests, the steady-state G 1 test and the yli I 1 test, to determine the ooling mode yli degradation oeffiient, C. If the two optional tests are not D onduted, assign seven tests. C the default value of Table 9 speifies test onditions for these D Table 9. Cooling Mode Test Conditions for Units Having a Variable-Speed Compressor Test Desription A 2 Test required (steady, wet oil) B 2 Test required (steady, wet oil) E V Test - required (steady, wet oil) B 1 Test required (steady, wet oil) F 1 Test required (steady, wet oil) G 1 Test - optional (steady, dry oil) I 1 Test - optional (yli, dry oil) Notes: Air Entering Indoor Unit Temperature Dry-Bulb F C Wet-Bulb F C Dry-Bulb F C Air Entering Outdoor Unit Temperature Wet-Bulb F C Compressor Speed (1) 23.9 (1) Maximum (1) 18.3 (1) Maximum (1) 20.6 (1) Intermediate (1) 18.3 (1) Minimum (1) 11.9 (1) Minimum (5) (5) Minimum Minimum Cooling Air Volume Rate Cooling Fullload (2) Cooling Fullload (2) Cooling Intermediate (3) Cooling Minimum (4) Cooling Minimum (4) Cooling Minimum (4) (6) (1) (2) (3) (4) (5) (6) The speified test ondition only applies if the unit rejets ondensate to the outdoor oil. Defined in setion Defined in setion Defined in setion The entering air must have a low enough moisture ontent so no ondensate forms on the indoor oil. (It is reommended that an indoor wet-bulb temperature of 57.0 F [13.9 C] or less be used.) Maintain the airflow nozzles stati pressure differene or veloity pressure during the ON period at the same pressure differene or veloity pressure as measured during the G 1 Test Heating Mode Tests For A Heat Pump Having A Variable-speed Compressor. a. Condut one maximum temperature test (H0 1 ), two high temperature tests (H1 2 and H1 1 ), one frost aumulation test (H2 V ), and one low temperature test (H3 2 ). Conduting one or both of the following tests is optional: an additional high temperature test (H1 N ) and an additional frost aumulation test (H2 2 ). Condut the optional maximum temperature h yli (H0C 1 ) test to determine the heating mode yli degradation oeffiient, C. If this optional test is not onduted, assign speifies test onditions for these eight tests. h C the default value of Table 10 D D 19

27 ANSI/AHRI STANDARD 210/ Table 10. Heating Mode Test Conditions for Units Having a Variable-Speed Compressor Test Desription H0 1 Test (required, steady) H0C 1 Test (optional, yli) H1 2 Test (required, steady) H1 1 Test (required, steady) H1 N Test (optional, steady) H2 2 Test (optional) H2 V Test (required) H3 2 Test (required, steady) Notes: Dry-Bulb F C Air Entering Indoor Unit Temperature Wet-Bulb F C Air Entering Outdoor Unit Temperature Dry-Bulb F C Wet-Bulb F C Compressor Speed (max) 15.6 (max) Minimum (max) 15.6 (max) Minimum (max) 15.6 (max) Maximum (max) 15.6 (max) Minimum (max) 15.6 (max) Cooling Mode Maximum (max) 15.6 (max) Maximum (max) 15.6 (max) Intermediate (max) 15.6 (max) Maximum Heating Air Volume Rate Heating Minimum (1) (2) Heating Fullload (3) Heating Minimum (1) Heating Nominal (4) Heating Fullload (3) Heating Intermediate (5) Heating Fullload (3) (1) (2) (3) (4) (5) Defined in setion Maintain the airflow nozzles stati pressure differene or veloity pressure during the ON period at the same pressure differene or veloity pressure as measured during the H0 1 Test. Defined in setion Defined in setion Defined in setion Table 11. Minimum External Stati Pressure for Duted Systems Tested with an Indoor Fan Installed Minimum External Resistane (3) Rated Cooling (1) or Heating (2) Capaity All Other Systems Small-Dut, High- Veloity Systems (4,5) Btu/h kw in H 2 O Pa in H 2 O Pa Up thru 28,800 Up thru ,000 to 42, to ,000 and Above 12.6 thru (1) For air onditioners and heat pumps, the value ited by the manufaturer in published literature for the unit s apaity when operated at the A or A 2 Test onditions. (2) For heating-only heat pumps, the value the manufaturer ites in published literature for the unit s apaity when operated at the H1 or H1 2 Test onditions. (3) For duted units tested without an air filter installed, inrease the appliable tabular value by 0.08 in H 2 O [20 Pa]. (4) See Definition 1.35 of Appendix C to determine if the equipment qualifies as a small-dut, high-veloity system. (5) If a losed-loop, air-enthalpy test apparatus is used on the indoor side, limit the resistane to airflow on the inlet side of the indoor blower oil to a maximum value of 0.10 in H 2 O [25 Pa]. Impose the balane of the airflow resistane on the outlet side of the indoor blower. 20

28 ANSI/AHRI STANDARD 210/ Table 12. Conditions for Standard Rating Tests and Operating Requirement Tests for Water-ooled and Evaporatively-ooled Equipment Using ASHRAE Standard 37 TEST INDOOR SECTION Air Entering Temperature Dry-Bulb Wet-Bulb OUTDOOR SECTION Evaporatively-ooled Water-ooled 2 Air Entering Temperature Air Entering Temperature Dry-Bulb Wet-Bulb Make-up Water 3 Condenser Inlet Condenser Outlet F C F C F C F C F C F C F C Standard Rating Conditions Cooling 1 Low Temperature Operating Cooling Insulation Effiieny COOLING Condensate Disposal Maximum Operating Conditions Part Load Conditions (IEER) Varies with load per Table 12A Varies with load per Table 12A Varies with load per Table 12A Varies with load per Table 12A Varies with load per Table 12A Notes: Part-Load Conditions (IPLV) Assume full load water flow rate so outlet temperature is a funtion of test Same onditions used for Voltage Tolerane Tests Water flow rate as determined from Standard Rating Conditions. Water in basin shall not overflow. 6.2 Part-Load Rating. Only systems whih are apable of apaity redution shall be rated at 100% and at eah step of apaity redution provided by the refrigeration system(s) as published by the manufaturer. These rating points shall be used to alulate the IPLV (see 6.2.2) Part-Load Rating Conditions. Test onditions for part-load ratings shall be per Table 12. Any water flow required for system funtion shall be at water flow rates established at (full load) Standard Rating Conditions. Capaity redution means may be adjusted to obtain the speified step of unloading. No manual adjustment of indoor and outdoor airflow rates from those of the Standard Rating Conditions shall be made. However, automati adjustment of airflow rates by system funtion is permissible Integrated Part-Load Value (IPLV). For equipment overed by this standard, the IPLV shall be alulated as follows: a. Determine the apaity and EER at the onditions speified in Table 12. b. Determine the part-load fator (PLF) from Figure 1 at eah rating point (see Appendix E).. Use the following equation to alulate IPLV: 21

29 ANSI/AHRI STANDARD 210/ EER + EER EER + EER IPLV = PLF PLF PLF PLF EER + EER n 1 n + PLF PLF PLF EER + n 1 n 2 n n where: PLF = Part-load fator determined from Figure 1 n Supersript 1 = Total number of apaity steps = 100% apaity and EER at part-load Rating Conditions Subsript 2, 3 et. = Speifi apaity and EER at part-load steps per Part-Load Rating. All unitary water-ooled and evaporatively-ooled units rated in aordane with this standard (not appliable to air-ooled Unitary Air Conditioners or Air-Soure Unitary Heat Pumps) shall inlude an Integrated Energy Effiieny Ratio (IEER), even if they have only one stage of ooling apaity ontrol General. The IEER is intended to be a measure of merit for the part-load performane of the unit. Eah building may have different part-load performane due to loal oupany shedules, building onstrution, building loation and ventilation requirements. For speifi building energy performane an hour-by-hour energy analysis program should be used Integrated Energy Effiieny Ratio (IEER). For equipment overed by this standard, the IEER shall be alulated using test derived data and the following formula. IEER = (0.020 A) + (0.617 B) + (0.238 C) + (0.125 D) 1 Where: A = EER at 100% net apaity at AHRI Standard Rating Conditions B = EER at 75% net apaity and redued air entering outdoor unit onditions (see Table 5) C = EER at 50% net apaity and redued air entering outdoor unit onditions (see Table 5) D = EER at 25% net apaity and redued air entering outdoor unit onditions (see Table 5) The IEER rating requires that the unit effiieny be determined at 100%, 75%, 50% and 25% load (net apaity) at the onditions speified in Table 5. If the unit, due to its apaity ontrol logi annot be operated at the 75%, 50%, or 25% load points, then the 75%, 50%, or 25% EER is determined by plotting the tested EER vs. the perent load and using straight line segments to onnet the atual performane points. Linear interpolation is used to determine the EER at 75%, 50% and 25% net apaity. For the interpolation, an atual apaity point equal to or less than the required rating point must be used to plot the urves. Extrapolation of the data is not allowed. If the unit annot be unloaded to the 75%, 50%, or 25% load then the unit should be run at the minimum step of unloading at the ondenser onditions defined for eah of the rating load points and then the effiieny should be adjusted for yli performane using the following equation. EER LF Net Capaity = LF [C (P + P )] + P + P D C CF IF CT 2 Where: 22 C D = The degradation oeffiient to aount for yling of the ompressor for apaity less than the minimum step of apaity. C D should be determined using equation 3. Net Capaity = Measured net apaity at the lowest mahine unloading point operating at the desired part-load Rating Condition, Btu/h

30 ANSI/AHRI STANDARD 210/ P C = Compressor power at the lowest mahine unloading point operating at the desired partload Rating Condition, watts P CF = For water-ooled equipment this is the total power allowane for ooling tower fan motor and irulating pump motor power as defined in Setion 6.1 at full load rating onditions. For evaporatively-ooled produts it is the power draw of the evaporatively fan and irulating pumps for the atual tested produt. P CT = Control iruit power and any auxiliary loads, watts P IF = Indoor fan motor power at the fan speed for the minimum step of apaity, watts C D = ( 0.13 LF) Where: LF is the frational on time for last stage at the desired load point. %Load (Full Load Unit Net Capaity) 100 LF = 4 Part Load Unit Net Capaity %Load = The standard rating point i.e. 75%, 50%, 25%. Table 12A. IEER Part-Load Rating Conditions CONDITIONS F C Indoor Air Return Air Dry-Bulb Temperature Return Air Wet-Bulb Temperature Indoor Airflow Rate Note 1 Condenser (Water-Cooled) Entering Condenser Water Temperature (EWT) For % Load > 34.8%, EWT = % LOAD + 39 For % Load 34.8%, EWT = Note 1 For % Load > 34.8%, EWT = % LOAD For % Load 34.8%, EWT = 12.8 Condenser Water Flow Rate (gpm) Condenser (Evaporatively-Cooled) Entering Wet-Bulb Temperature (EWB) Entering Dry-Bulb Temperature (EDB) full load flow For % Load > 36.6%, EWB = 0.35 % Load + 40 For % Load 36.6%, EWB = 52.8 For % Load >44.4% EDB=0.54 % Load +41 For % Load 44.4%, EDB= 65.0 full load flow For % Load > 36.6%, EWB = 0.19 % Load For % Load 36.6%, EWB = 11.6 For % Load >44.4% EDB=0.30 % Load +5.0 For % Load 44.4%, EDB= 18.3 Note: 1 For fixed speed indoor fans the airflow rate should be held onstant at the full load airflow rate. For VAV units the airflow rate at part load should be adjusted to maintain the full load measured leaving air drybulb temperature and the external stati pressure should be redued per the following equation. The tolerane for the leaving air dry-bulb temperature on VAV units is ±0.3 F [±0.2 C]. For units using disrete step fan ontrol, the fan speed should be adjusted as speified by the ontrols and the external stati pressure should be redued per the following equation. ExternalSt ati = FullLoadExternalStati ( PartLoadCFM ) 2 FullLoadCFM 23

31 ANSI/AHRI STANDARD 210/ Example 1 Water-ooled unit with proportional apaity ontrol and an be run at the 75%, 50%, and 25% rating points and has a fixed speed indoor fan. Assume that the unit has the following measured performane Stage EWT Atual % Load (Net Cap) Gross Capaity Net Capaity Cmpr (P C ) Tower (PCF) Indoor (P IF ) Control (P CT ) (F) % Btu/h Btu/h W W W W Btu/(W h) ,000 52,065 3, ,984 39,049 1, ,459 19, ,951 13, EER Using the measured performane you an then alulate the IEER as follows: IEER = ( ) + ( ) + ( ) + ( ) = Using the round off requirements, the unit would have a apaity rating of 52,000 Btu/h, an EER rating of 12.1, and an IEER rating of Example 2 Water-ooled unit with a single ompressor and a fixed speed indoor fan. Assume the unit has the following tested performane. Stage EWT Atual % Load (Net Cap) The example 2 unit only has one stage of apaity ontrol so it annot unload. Therefore four tests have been run at the rating points for 75%, 50% and 25% load ondenser water onditions and then as shown below the performane has to be adjusted for the yli performane using the requirements of The following is an example of the CD alulations for the 50% load point ,065 LF = 100 = ,789 Gross Capaity Net Capaity Cmpr (P C ) Tower (P CF) Indoor (P IF ) Control (P CT ) (F) % Btu/h Btu/h W W W W Btu/(W h) ,000 52,065 3, ,900 54,965 2, ,724 57,789 2, ,096 59,161 2, Stage EWT Atual % Load (Net Cap) Gross Capaity Net Capaity Cmpr Tower (P ) C (P CF ) Indoor (P IF ) Control (P CT ) EER EER C D LF (F) % Btu/h Btu/h W W W W Btu/(W h) ,000 52,065 3, ,900 54,965 2, Adjusted for Cyli Performane ,724 57,789 2, Adjusted for Cyli Performane ,096 59,161 2,

32 ANSI/AHRI STANDARD 210/ C D = ( ) = EER 50% = , [1.071 (2, )] = Using the above post test alulations shown in the table the IEER alulations are shown in the following equation. IEER = ( ) + ( ) + ( ) + ( ) = Using the round off requirements, the unit would have a apaity rating of 52,000 Btu/h, an EER rating of 12.1, and an IEER rating of Example 3 Water ooled unit with 2 stages of apaity and a 2 speed indoor fan that operates on low speed during operating of stage 1 Assume the following tested performane; Stage EWT Atual % Load (Net Cap) Gross Capaity To obtain the rating for the 75% rating point interpolation between the stage 2 and stage 1 performane is required beause the stage 1 apaity is 71% whih is less than the 75% rating point. For the 50% and 25% rating point the unit annot unload to these levels and therefore the CD fator must be used. The details are shown in the following table. Based on this then the IEER an be alulated as shown below. IEER = ( ) + ( ) + ( ) + ( ) = Using the round off requirements, the unit would have a apaity rating of 52,000 Btu/h, an EER rating of 12.1, and an IEER rating of Example 4 Evaporatively-ooled unit with 2 stages of apaity and a 2 speed indoor fan where the fan operates on low speed during operation of stage 1. Assume the following tested performane: Net Capaity Cmpr (P C ) Tower (PCF) Indoor (P IF ) Control (P CT ) (F) % Btu/h Btu/h W W W W Btu/(W h) ,000 52,065 3, ,740 36,966 1, ,613 38,839 1, ,523 39,749 1, Stage EWT Atual % Load (Net Cap) Gross Capaity Net Capaity Cmpr Tower (P ) C (P CF ) Indoor (P IF ) Control (P CT ) EER EER C D LF (F) % Btu/h Btu/h W W W W Btu/(W h) ,000 52,065 3, ,740 36,966 1, interpolation ,613 38,839 1, Adjusted for Cyli Performane ,523 39,749 1,

33 ANSI/AHRI STANDARD 210/ Stage EDB EWB Atual % Load (Net Cap) Gross Capaity Net Capaity To obtain the rating for the 75% rating point interpolation between the stage 2 and stage 1 performane is required beause the stage 1 apaity us 71% whih is less than the 75% rating point. For the 50% and 25% rating points the unit an not unload to these levels and therefore the CD fator must be used. The details are shown in the following table. Stage EDB OAT EWB Atual % Gross Net Cmpr Evap Indoor Control EER C D LF Load (Net Cap) Capaity Capaity (P C ) Cond (PCF) (P IF ) (P CT ) F F % Btu/h Btu/h W W W W Btu/(W h) ,065 3, ,966 1, Interpolation ,839 1, Adjusted for Cyli Performane ,749 1, Based on this then the IEER an be alulated as shown below. IEER = ( ) + ( ) + ( ) + ( ) = Using the round off requirements, the unit would have a apaity rating of 52,000 Btu/h, an EER rating of 12.1, and an IEER rating of Appliation Ratings. Ratings at onditions of temperature or airflow rate other than those speified in and may be published as Appliation Ratings, and shall be based on data determined by the methods presribed in 6.1. Appliation Ratings in the defrost region shall inlude net apaity and COP based upon a omplete defrost yle. 6.4 Publiation of Ratings. Wherever Appliation Ratings are published or printed, they shall inlude, or be aompanied by the Standard Ratings, plus the IEER (where appliable), plus the IPLV (where appliable), learly designated as suh, inluding a statement of the onditions at whih the ratings apply Capaity Designation. The apaity designation used in published speifiations, literature or advertising, ontrolled by the manufaturer, for equipment rated under this standard, shall be expressed only in Btu/h [W] at the Standard Rating Conditions speified in plus part-load Rating Conditions speified in and in the terms desribed in and Horsepower, tons or other units shall not be used as apaity designation. 6.5 Toleranes. To omply with this standard, measured test results shall not be less than 95% of Published Ratings for performane ratios and apaities, exept IEER whih shall not be less than 90% of Published Ratings. Note: Residential and ommerial produts overed under the Energy Poliy and Conservation At (EPCA) shall be rated in aordane with 10 CFR setion 16 and setion 43 respetively. Cmpr (P C ) Evap Cond (P CF ) Indoor (P IF ) Control (P CT ) F F % Btu/h Btu/h W W W W Btu/(W h) ,000 52,065 3, ,740 36,966 1, ,613 38,839 1, ,523 39,749 1, EER 26

34 ANSI/AHRI STANDARD 210/ Setion 7. Minimum Data Requirements for Published Ratings 7.1 Minimum Data Requirements For Published Ratings. As a minimum, Published Ratings shall onsist of the following information: a. For Unitary Air-Conditioners (air-ooled) 1. AHRI standard rating ooling apaity 2. Seasonal Energy Effiieny Ratio, SEER b. For Unitary Air-Conditioners (water-ooled and evaporatively-ooled) 1. AHRI standard rating ooling apaity 2. Energy Effiieny Ratio, EER 3. Integrated Energy Effiieny Ratio, IEER. For all Air-Soure Unitary Heat Pumps 1. AHRI standard rating ooling apaity 2. Seasonal Energy Effiieny Ratio, SEER 3. High temperature heating standard rating apaity 4. Region IV Heating Seasonal Performane Fator, HSPF, minimum design heating requirement 7.2 Latent Capaity Designation. The moisture removal designation shall be published in the manufaturer s speifiations and literature. The value shall be expressed onsistently in either gross or net in one or more of the following forms: a. Sensible apaity/total apaity ratio and total apaity b. Latent apaity and total apaity. Sensible apaity and total apaity 7.3 Rating Claims. All laims to ratings within the sope of this standard shall inlude the statement Rated in aordane with ANSI/AHRI Standard 210/240. All laims to ratings outside the sope of this standard shall inlude the statement: Outside the sope of ANSI/AHRI Standard 210/240. Wherever Appliation Ratings are published or printed, they shall inlude a statement of the onditions at whih the ratings apply. Setion 8. Operating Requirements 8.1 Operating Requirements. Unitary equipment shall omply with the provisions of this setion suh that any prodution unit will meet the requirements detailed herein. 8.2 Maximum Operating Conditions Test. Unitary equipment shall pass the following maximum operating onditions test with an indoor-oil airflow rate as determined under Temperature Conditions. Temperature onditions shall be maintained as shown in Tables 12 or

35 ANSI/AHRI STANDARD 210/ Table 13. Conditions for Operating Requirement Tests for Air-ooled Equipment TEST INDOOR UNIT Air Entering Temperature Dry-Bulb F C Wet-Bulb F C OUTDOOR UNIT Air Entering Temperature Dry-Bulb F C Wet-Bulb F C Voltage Tolerane COOLING Low Temperature Operation Cooling Insulation Effiieny Condensate Disposal Maximum Operating Conditions HEATING Notes: Voltage Tolerane (Heating-only units) (max) Maximum Operating Conditions The wet-bulb temperature ondition is not required when testing air-ooled ondensers whih do not evaporate ondensate Voltages. The test shall be run at the Range A minimum utilization voltage from AHRI Standard 110, Table 1, based upon the unit's nameplate rated voltage(s). This voltage shall be supplied at the unit's servie onnetion and at rated frequeny Proedure. The equipment shall be operated for one hour at the temperature onditions and voltage speified Requirements. The equipment shall operate ontinuously without interruption for any reason for one hour Units with water-ooled ondensers shall be apable of operation under these maximum onditions at a water- pressure drop not to exeed 15.0 psi [103 kpa], measured aross the unit. 8.3 Voltage Tolerane Test. Unitary equipment shall pass the following voltage tolerane test with a ooling oil airflow rate as determined under Temperature Conditions. Temperature onditions shall be maintained at the standard ooling (and/or standard heating, as required) steady state onditions as shown in Tables 12 or Voltages Tests shall be run at the Range B minimum and maximum utilization voltages from AHRI Standard 110, Table 1, based upon the unit's nameplate rated voltage(s). These voltages shall be supplied at the unit's servie onnetion and at rated frequeny. A lower minimum or a higher maximum voltage shall be used, if listed on the nameplate. 28

36 ANSI/AHRI STANDARD 210/ The power supplied to single phase equipment shall be adjusted just prior to the shut-down period ( ) so that the resulting voltage at the unit's servie onnetion is 86% of nameplate rated voltage when the ompressor motor is on loked-rotor. (For 200V or 208V nameplate rated equipment the restart voltage shall be set at 180V when the ompressor motor is on loked rotor). Open iruit voltage for threephase equipment shall not be greater than 90% of nameplate rated voltage Within one minute after the equipment has resumed ontinuous operation ( ), the voltage shall be restored to the values speified in Proedure The equipment shall be operated for one hour at the temperature onditions and voltage(s) speified All power to the equipment shall be shut off for a period suffiient to ause the ompressor to stop (not to exeed five seonds) and then restored Requirements During both tests, the equipment shall operate without failure of any of its parts The equipment shall operate ontinuously without interruption for any reason for the one hour period preeding the power interruption The unit shall resume ontinuous operation within two hours of restoration of power and shall then operate ontinuously for one half hour. Operation and resetting of safety devies prior to establishment of ontinuous operation is permitted. 8.4 Low-Temperature Operation Test (Cooling) (Not Required For Heating-only Units). Unitary equipment shall pass the following low-temperature operation test when operating with initial airflow rates as determined in and and with ontrols and dampers set to produe the maximum tendeny to frost or ie the evaporator, provided suh settings are not ontrary to the manufaturer's instrutions to the user Temperature Conditions. Temperature Conditions shall be maintained as shown in Table 12 or Table Proedure. The test shall be ontinuous with the unit on the ooling yle, for not less than four hours after establishment of the speified temperature onditions. The unit will be permitted to start and stop under ontrol of an automati limit devie, if provided Requirements During the entire test, the equipment shall operate without damage or failure of any of its parts During the entire test, the air quantity shall not drop more than 25% from that determined under the Standard Rating test During the test and during the defrosting period after the ompletion of the test, all ie or meltage must be aught and removed by the drain provisions. 29

37 ANSI/AHRI STANDARD 210/ Insulation Effetiveness Test (Cooling) (not required for heating-only units). Unitary equipment shall pass the following insulation effetiveness test when operating with airflow rates as determined in and with ontrols, fans, dampers, and grilles set to produe the maximum tendeny to sweat, provided suh settings are not ontrary to the manufaturer's instrutions to the user Temperature Conditions. Temperature onditions shall be maintained as shown in Table 12 or Table Proedure. After establishment of the speified temperature onditions, the unit shall be operated ontinuously for a period of four hours Requirements. During the test, no ondensed water shall drop, run, or blow off from the unit asing. 8.6 Condensate Disposal Test (Cooling)* (not required for heating-only units). Unitary equipment whih rejets ondensate to the ondenser air shall pass the following ondensate disposal test when operating with airflow rates as determined in and and with ontrols and dampers set to produe ondensate at the maximum rate, provided suh settings are not ontrary to the manufaturer's instrutions to the user. * This test may be run onurrently with the Insulation Effetiveness Test (8.5) Temperature Conditions. Temperature onditions shall be maintained as shown in Table 12 or Table Proedure. After establishment of the speified temperature onditions, the equipment shall be started with its ondensate olletion pan filled to the overflowing point and shall be operated ontinuously for four hours after the ondensate level has reahed equilibrium Requirements. During the test, there shall be no dripping, running-off, or blowing-off of moisture from the unit asing. 8.7 Toleranes. The onditions for the tests outlined in Setion 8 are average values subjet to toleranes of ± 1.0 F [± 0.6 C] for air wet-bulb and dry-bulb temperatures and ± 1.0% of the reading for voltages. Setion 9. Marking and Nameplate Data 9.1 Marking and Nameplate Data. As a minimum, the nameplate shall display the manufaturer's name, model designation, and eletrial harateristis. Nameplate voltages for 60 Hertz systems shall inlude one or more of the equipment nameplate voltage ratings shown in Table 1 of AHRI Standard 110. Nameplate voltages for 50 Hertz systems shall inlude one or more of the utilization voltages shown in Table 1 of IEC Standard Setion 10. Conformane Conditions 10.1 Conformane. While onformane with this standard is voluntary, onformane shall not be laimed or implied for produts or equipment within the standard s Purpose (Setion 1) and Sope (Setion 2) unless suh produt laims meet all of the requirements of the standard and all of the testing and rating requirements are measured and reported in omplete ompliane with the standard. Any produt that has not met all the requirements of the standard shall not referene, state, or aknowledge the standard in any written, oral, or eletroni ommuniation. 30

38 ANSI/AHRI STANDARD 210/ APPENDIX A. REFERENCES NORMATIVE A1 Listed here are all standards, handbooks and other publiations essential to the formation and implementation of the standard. All referenes in this appendix are onsidered as part of this standard. A1.1 ANSI/ASHRAE Standard , Methods of Testing for Rating Unitary Air-Conditioning and Heat Pump Equipment, 2005, Amerian Soiety of Heating, Refrigerating and Air-Conditioning Engineers, In., 1791 Tullie Cirle N.E., Atlanta, GA 30329, U.S.A. A1.2 ANSI/ASHRAE Standard (RA 2006), Standard Method for Temperature Measurement, 2006, Amerian Soiety of Heating, Refrigerating and Air-Conditioning Engineers, In., 1791 Tullie Cirle, N.E., Atlanta, GA 30329, U.S.A. A1.3 ANSI/ASHRAE Standard /AMCA Standard , Laboratory Methods of Testing Fans for Aerodynami Performane Rating, 1999, Amerian Soiety of Heating, Refrigerating and Air-Conditioning Engineers, In., 1791 Tullie Cirle, N.E., Atlanta, GA 30329, U.S.A. A1.4 AHRI Standard (formerly ARI Standard ), Air-Conditioning and Refrigerating Equipment Nameplate Voltages, Air-Conditioning, Heating, and Refrigeration Institute, 2002, 2111 Wilson Boulevard, Suite 500, Arlington, VA 22201, U.S.A. A1.5 AHRI Standard 210/ (formerly ARI Standard 210/ ), Unitary Air-Conditioning and Air- Soure Heat Pump Equipment, 2003, Air-Conditioning, Heating, and Refrigeration Institute, 2111 Wilson Boulevard, Suite 500, Arlington, VA 22201, U.S.A. A1.6 AHRI Standard 210/ (formerly ARI Standard 210/ ), Unitary Air-Conditioning and Air- Soure Heat Pump Equipment, 2006, Air-Conditioning, Heating, and Refrigeration Institute, 2111 Wilson Boulevard, Suite 500, Arlington, VA 22201, U.S.A. A1.7 AHRI Standard 340/ (formerly ARI Standard 340/ ), Commerial and Industrial Unitary Air-Conditioning and Heat Pump Equipment, 2007, Air-Conditioning, Heating, and Refrigeration Institute, 2111 Wilson Boulevard, Suite 500, Arlington, VA 22201, U.S.A. A1.8 ASHRAE Standard , Methods of Testing for Rating Positive Displaement Refrigerant Compressors and Condensing Units, 1993, Amerian Soiety of Heating, Refrigerating and Air-Conditioning Engineers, In., 1791 Tullie Cirle, N.E., Atlanta, GA 30329, U.S.A. A1.9 ASHRAE Standard , Methods of Testing for Rating Unitary Air-Conditioning and Heat Pump Equipment, 1988, Amerian Soiety of Heating, Refrigerating and Air-Conditioning Engineers, In., 1791 Tullie Cirle, N.E., Atlanta, GA 30329, U.S.A. A1.10 ASHRAE Standard (RA 1992), Standard Methods for Laboratory Airflow Measurement, 1992, Amerian Soiety of Heating, Refrigerating and Air-Conditioning Engineers, In., 1791 Tullie Cirle, N.E., Atlanta, GA 30329, U.S.A. A1.11 ASHRAE Standard (RA 2001), Method for Measurement of Moist Air Properties, 2001, Amerian Soiety of Heating, Refrigerating and Air-Conditioning Engineers, In., 1791 Tullie Cirle, N.E., Atlanta, GA 30329, U.S.A. A1.12 ASHRAE Standard , Calorimeter Test Methods for Mass Flow Measurements of Volatile Refrigerants, 2000, Amerian Soiety of Heating, Refrigerating and Air-Conditioning Engineers, In., 1791 Tullie Cirle, N.E., Atlanta, GA 30329, U.S.A. A1.13 ASHRAE Terminology of Heating, Ventilation, Air-Conditioning and Refrigeration, Seond Edition, 1991, Amerian Soiety of Heating, Refrigerating and Air-Conditioning Engineers, In., 1791 Tullie Cirle, N.E., Atlanta, GA 30329, U.S.A. 31

39 ANSI/AHRI STANDARD 210/ A1.14 IEC Standard 60038, IEC Standard Voltages, 2002, International Eletrotehnial Commission, 3, rue de Varembe, P.O. Box 131, 1211 Geneva 20, Switzerland. A1.15 Title 10, Code of Federal Regulations (CFR), Part 430, Subparts and (), U.S. National Arhives and Reords Administration, 8601 Adelphi Road, College Park, MD APPENDIX B. REFERENCES INFORMATIVE B1 Listed here are standards, handbooks and other publiations whih may provide useful information and bakground but are not onsidered essential. Referenes in this appendix are not onsidered part of the standard. B1.1 ANSI/ASHRAE Standard (RA 05), Methods of Testing for Rating for Seasonal Effiieny of Unitary Air Conditioners and Heat Pumps, 2005, Amerian Soiety of Heating, Refrigerating and Air-Conditioning Engineers, In., 1791 Tullie Cirle, N.E., Atlanta, GA 30329, U.S.A. 32

40 ANSI/AHRI STANDARD 210/ APPENDIX C. UNIFORM TEST METHOD FOR MEASURING THE ENERGY CONSUMPTION OF CENTRAL AIR CONDITIONERS AND HEAT PUMPS NORMATIVE Foreword: This appendix to ANSI/AHRI standard 210/ is the Uniform Test Method for Measuring the Energy Consumption of Central Air Conditioners and Heat Pumps Appendix M to Subpart B of Part 430, pages through 59180, Federal Register, Vol. 70, No. 195, Tuesday, Otober 11, 2005 as amended by the Federal Register, Vol. 72, No. 203, Monday, Otober 22, 2007 pages through APPENDIX M to Subpart B of Part 430 Uniform Test Method for Measuring the Energy Consumption of Central Air Conditioners and Heat Pumps Eletroni Code of Federal Regulations (e-cfr) BETA TEST SITE e-cfr Data is urrent as of February 9, 2006 Amendment from Otober 11, CFR--PART 430 Amendment(s) published Otober 11, 2005, in 70 FR Effetive Date(s): April 10, Appendix M to Subpart B is revised to read as follows: Appendix M to Subpart B of Part 430 Uniform Test Method for Measuring the Energy Consumption of Central Air Conditioners and Heat Pumps 33

41 ANSI/AHRI STANDARD 210/ DEFINITIONS 2. TESTING CONDITIONS 2.1 Test room requirements. 2.2 Test unit installation requirements Defrost ontrol settings Speial requirements for units having a multiple-speed outdoor fan Speial requirements for multi-split air onditioners and heat pumps, and systems omposed of multiple mini-split units (outdoor units loated side-by-side) that would normally operate using two or more indoor thermostats Wet-bulb temperature requirements for the air entering the indoor and outdoor oils Cooling mode tests Heating mode tests Additional refrigerant harging requirements. 2.3 Indoor air volume rates Cooling tests Heating tests. 2.4 Indoor oil inlet and outlet dut onnetions Outlet plenum for the indoor unit Inlet plenum for the indoor unit. 2.5 Indoor oil air property measurements and air damper box appliations Test set-up on the inlet side of the indoor oil: For ases where the inlet damper box is installed If the setion inlet plenum is installed If the setion inlet plenum is not installed Test set-up on the inlet side of the indoor unit: For ases where no inlet damper box is installed Indoor oil stati pressure differene measurement Test set-up on the outlet side of the indoor oil Outlet air damper box plaement and requirements Proedures to minimize temperature maldistribution Minimizing air leakage. 34

42 ANSI/AHRI STANDARD 210/ Dry bulb temperature measurement Water vapor ontent measurement Air damper box performane requirements. 2.6 Airflow measuring apparatus. 2.7 Eletrial voltage supply. 2.8 Eletrial power and energy measurements. 2.9 Time measurements Test apparatus for the seondary spae onditioning apaity measurement Outdoor Air Enthalpy Method Compressor Calibration Method Refrigerant Enthalpy Method Measurement of test room ambient onditions Measurement of indoor fan speed Measurement of barometri pressure. 3. TESTING PROCEDURES 3.1 General Requirements Primary and seondary test methods Manufaturer-provided equipment overrides Airflow through the outdoor oil Airflow through the indoor oil Cooling Full-Load Air Volume Rate Cooling Full-Load Air Volume Rate for Duted Units Cooling Full-Load Air Volume Rate for Non-duted Units Cooling Minimum Air Volume Rate Cooling Intermediate Air Volume Rate Heating Full-Load Air Volume Rate Duted heat pumps where the Heating and Cooling Full-Load Air Volume Rates are the same. 35

43 ANSI/AHRI STANDARD 210/ Duted heat pumps where the Heating and Cooling Full-Load Air Volume Rates are different due to indoor fan operation Duted heating-only heat pumps Non-duted heat pumps, inluding non-duted heating-only heat pumps Heating Minimum Air Volume Rate Heating Intermediate Air Volume Rate Heating Nominal Air Volume Rate Indoor test room requirement when the air surrounding the indoor unit is not supplied from the same soure as the air entering the indoor unit Air volume rate alulations Test sequene Requirement for the air temperature distribution leaving the indoor oil Control of auxiliary resistive heating elements. 3.2 Cooling mode tests for different types of air onditioners and heat pumps Tests for a unit having a single-speed ompressor that is tested with a fixed-speed indoor fan installed, with a onstantair-volume-rate indoor fan installed, or with no indoor fan installed Tests for a unit having a single-speed ompressor and a variable-speed variable-air-volume-rate indoor fan installed Indoor fan apaity modulation that orrelates with the outdoor dry bulb temperature Indoor fan apaity modulation based on adjusting the sensible to total (S/T) ooling apaity ratio Tests for a unit having a two-apaity ompressor Tests for a unit having a variable-speed ompressor. 3.3 Test proedures for steady-state wet oil ooling mode tests (the A, A 2, A 1, B, B 2, B 1, E V, and F 1 Tests). 3.4 Test proedures for the optional steady-state dry oil ooling mode tests (the C, C 1, and G 1 Tests). 3.5 Test proedures for the optional yli dry oil ooling mode tests (the D, D 1, and I 1 Tests) Proedures when testing duted systems Proedures when testing non-duted systems Cooling mode yli degradation oeffiient alulation. 3.6 Heating mode tests for different types of heat pumps, inluding heating-only heat pumps. 36

44 ANSI/AHRI STANDARD 210/ Tests for a heat pump having a single-speed ompressor that is tested with a fixed speed indoor fan installed, with a onstant-air-volume-rate indoor fan installed, or with no indoor fan installed Tests for a heat pump having a single-speed ompressor and a variable-speed, variable-air-volume-rate indoor fan: apaity modulation orrelates with outdoor dry bulb temperature Tests for a heat pump having a two-apaity ompressor (see Definition 1.45), inluding two-apaity, northern heat pumps (see Definition 1.46) Tests for a heat pump having a variable-speed ompressor Additional test for a heat pump having a heat omfort ontroller. 3.7 Test proedures for steady-state Maximum Temperature and High Temperature heating mode tests (the H0 1, H1, H1 2, H1 1, and H1 N Tests). 3.8 Test proedures for the optional yli heating mode tests (the H0C 1, H1C, and H1C 1 Tests) Heating mode yli degradation oeffiient alulation. 3.9 Test proedures for Frost Aumulation heating mode tests (the H 2, H2 2, H2 V, and H2 1 Tests) Average spae heating apaity and eletrial power alulations Demand defrost redit Test proedures for steady-state Low Temperature heating mode tests (the H 3, H3 2, and H3 1 Tests) Additional requirements for the seondary test methods If using the Outdoor Air Enthalpy Method as the seondary test method If a preliminary test preedes the offiial test If a preliminary test does not preede the offiial test Offiial test If using the Compressor Calibration Method as the seondary test method If using the Refrigerant Enthalpy Method as the seondary test method Rounding of spae onditioning apaities for reporting purposes. 4. CALCULATIONS OF SEASONAL PERFORMANCE DESCRIPTORS 4.1 Seasonal Energy Effiieny Ratio (SEER) Calulations SEER alulations for an air onditioner or heat pump having a single-speed ompressor that was tested with a fixedspeed indoor fan installed, a onstant-air-volume-rate indoor fan installed, or with no indoor fan installed SEER alulations for an air onditioner or heat pump having a single-speed ompressor and a variable-speed variable-air-volume-rate indoor fan. 37

45 ANSI/AHRI STANDARD 210/ Units overed by setion where indoor fan apaity modulation orrelates with the outdoor dry bulb temperature Units overed by setion where indoor fan apaity modulation is used to adjust the sensible to total ooling apaity ratio SEER alulations for an air onditioner or heat pump having a two-apaity ompressor Steady-state spae ooling apaity at low ompressor apaity is greater than or equal to the building ooling load at temperature T j, Q k=1 (T j ) BL(T j ) Unit alternates between high (k=2) and low (k=1) ompressor apaity to satisfy the building ooling load at temperature T j, Q k=1 (T j ) < BL(T j ) < Q k=2 (T j ) Unit only operates at high (k=2) ompressor apaity at temperature T j and its apaity is greater than the building ooling load, BL(T j ) < Q k=2 (T j ) Unit must operate ontinuously at high (k=2) ompressor apaity at temperature T j, BL(T j ) Q k=2 (T j ) SEER alulations for an air onditioner or heat pump having a variable-speed ompressor Steady-state spae ooling apaity when operating at minimum ompressor speed is greater than or equal to the building ooling load at temperature T j, Q k=1 (T j ) BL(T j ) Unit operates at an intermediate ompressor speed (k=i) in order to math the building ooling load at temperature T j, Q k=1 (T j ) < BL(T j ) < Q k=2 (T j ) Unit must operate ontinuously at maximum (k=2) ompressor speed at temperature T j, BL(T j ) Q k=2 (T j ). 4.2 Heating Seasonal Performane Fator (HSPF) Calulations Additional steps for alulating the HSPF of a heat pump having a single-speed ompressor that was tested with a fixed-speed indoor fan installed, a onstant-air-volume-rate indoor fan installed, or with no indoor fan installed Additional steps for alulating the HSPF of a heat pump having a single-speed ompressor and a variable-speed, variable-air-volume-rate indoor fan Additional steps for alulating the HSPF of a heat pump having a two-apaity ompressor Steady-state spae heating apaity when operating at low ompressor apaity is greater than or equal to the building heating load at temperature T j, Q h k=1 (T j ) BL(T j ) Heat pump alternates between high (k=2) and low (k=1) ompressor apaity to satisfy the building heating load at a temperature T j, Q h k=1 (T j ) BL (T j ) < Q h k=2 (T j ) Heat pump only operates at high (k=2) ompressor apaity at temperature T j and its apaity is greater than the building heating load, BL(T j ) < Q h k=2 (T j ) Heat pump must operate ontinuously at high (k=2) ompressor apaity at temperature T j, BL(T j ) Q h k=2 (T j ). 38

46 4.2.4 Additional steps for alulating the HSPF of a heat pump having a variable-speed ompressor. ANSI/AHRI STANDARD 210/ Steady-state spae heating apaity when operating at minimum ompressor speed is greater than or equal to the building heating load at temperature T j, Q h k=1 (T j ) BL(T j ) Heat pump operates at an intermediate ompressor speed (k=i) in order to math the building heating load at a temperature T j, Q h k=1 (T j ) < BL(T j ) < Q h k=2 (T j ) Heat pump must operate ontinuously at maximum (k=2) ompressor speed at temperature T j, BL(T j ) Q h k=2 (T j ) Heat pumps having a heat omfort ontroller Heat pump having a heat omfort ontroller: Additional steps for alulating the HSPF of a heat pump having a single-speed ompressor that was tested with a fixed-speed indoor fan installed, a onstant-air-volume-rate indoor fan installed, or with no indoor fan installed Heat pump having a heat omfort ontroller: Additional steps for alulating the HSPF of a heat pump having a single-speed ompressor and a variable-speed, variable-air-volume-rate indoor fan Heat pumps having a heat omfort ontroller: Additional steps for alulating the HSPF of a heat pump having a twoapaity ompressor Heat pumps having a heat omfort ontroller: Additional steps for alulating the HSPF of a heat pump having a variable-speed ompressor. [Reserved] 4.3 Calulations of the Atual and Representative Regional Annual Performane Fators for Heat Pumps Calulation of atual regional annual performane fators (APF A ) for a partiular loation and for eah standardized design heating requirement Calulation of representative regional annual performane fators (APF R ) for eah generalized limati region and for eah standardized design heating requirement. 4.4 Rounding of SEER, HSPF, and APF for reporting purposes. 1. Definitions 1.1 Annual performane fator means the total heating and ooling done by a heat pump in a partiular region in one year divided by the total eletri energy used in one year. Paragraph (m)(3)(iii) of of the Code of Federal Regulations states the alulation requirements for this rating desriptor. 1.2 AHRI means Air-Conditioning and Refrigeration Institute. 1.3 AHRI Standard 210/ means the test standard Unitary Air-Conditioning and Air-Soure Heat Pump Equipment published in 2006 by AHRI. 1.4 ASHRAE means the Amerian Soiety of Heating, Refrigerating and Air-Conditioning Engineers, In. 1.5 ASHRAE Standard means the test standard Methods of Testing for Rating Positive Displaement Refrigerant Compressors and Condensing Units published in 2005 by ASHRAE. 1.6 ASHRAE Standard means the test standard Methods of Testing for Rating Unitary Air-Conditioning and Heat Pump Equipment published in 2005 by ASHRAE. 39

47 ANSI/AHRI STANDARD 210/ ASHRAE Standard (RA 01) means the test standard Standard Method for Temperature Measurement published in 1986 and reaffirmed in 2001 by ASHRAE. 1.8 ASHRAE Standard (RA 92) means the test standard Standard Methods for Laboratory Airflow Measurement published in 1987 and reaffirmed in 1992 by ASHRAE. 1.9 ASHRAE Standard (RA 01) means the test standard Method for Measurement of Moist Air Properties published in 1994 and reaffirmed in 2001 by ASHRAE ASHRAE Standard means the test standard Calorimeter Test Methods for Mass Flow Measurements of Volatile Refrigerants published in 2000 by ASHRAE ASHRAE Standard 51 99/AMCA Standard means the test standard Laboratory Methods of Testing Fans for Aerodynami Performane Rating published in 1999 by ASHRAE and the Air Movement and Control Assoiation International, In ASHRAE Standard (RA05) means the test standard Methods of Testing for Rating for Seasonal Effiieny of Unitary Air Conditioners and Heat Pumps published in 1995 and reaffirmed in 2005 by ASHRAE CFR means Code of Federal Regulations Constant-air-volume-rate indoor fan means a fan that varies its operating speed to provide a fixed air-volume-rate from a duted system Continuously reorded, when referring to a dry bulb measurement, means that the speified temperature must be sampled at regular intervals that are equal to or less than the maximum intervals speified in setion 4.3 part a of ASHRAE Standard (RA 01). If suh dry bulb temperatures are used only for test room ontrol, it means that one samples at regular intervals equal to or less than the maximum intervals speified in setion 4.3 part b of the same ASHRAE Standard. Regarding wet bulb temperature, dew point temperature, or relative humidity measurements, ontinuously reorded means that the measurements must be made at regular intervals that are equal to or less than 1 minute Cooling load fator (CLF) means the ratio having as its numerator the total ooling delivered during a yli operating interval onsisting of one ON period and one OFF period. The denominator is the total ooling that would be delivered, given the same ambient onditions, had the unit operated ontinuously at its steady-state spae ooling apaity for the same total time (ON + OFF) interval Coeffiient of Performane (COP) means the ratio of the average rate of spae heating delivered to the average rate of eletrial energy onsumed by the heat pump. These rate quantities must be determined from a single test or, if derived via interpolation, must be tied to a single set of operating onditions. COP is a dimensionless quantity. When determined for a duted unit tested without an indoor fan installed, COP must inlude the setion 3.7, 3.8, and default values for the heat output and power input of a fan motor Cyli Test means a test where the unit's ompressor is yled on and off for speifi time intervals. A yli test provides half the information needed to alulate a degradation oeffiient Damper box means a short setion of dut having an air damper that meets the performane requirements of setion Degradation oeffiient (C D ) means a parameter used in alulating the part load fator. The degradation oeffiient for ooling is denoted by C D. The degradation oeffiient for heating is denoted by C D h Demand-defrost ontrol system means a system that defrosts the heat pump outdoor oil only when measuring a predetermined degradation of performane. The heat pump's ontrols monitor one or more parameters that always vary with the amount of frost aumulated on the outdoor oil (e.g., oil to air differential temperature, oil differential air pressure, outdoor fan power or urrent, optial sensors, et.) at least one for every ten minutes of ompressor ON-time when spae heating. One aeptable alternative to the riterion given in the prior sentene is a feedbak system that measures the length of the defrost period and adjusts defrost frequeny aordingly. 1 In all ases, when the frost parameter(s) reahes a 40

48 ANSI/AHRI STANDARD 210/ predetermined value, the system initiates a defrost. In a demand-defrost ontrol system, defrosts are terminated based on monitoring a parameter(s) that indiates that frost has been eliminated from the oil. 1 Systems that vary defrost intervals aording to outdoor dry-bulb temperature are not demand defrost systems. A demand-defrost ontrol system, whih otherwise meets the above requirements, may allow time-initiated defrosts if, and only if, suh defrosts our after 6 hours of ompressor operating time Design heating requirement (DHR) predits the spae heating load of a residene when subjeted to outdoor design onditions. Estimates for the minimum and maximum DHR are provided for six generalized U.S. limati regions in setion Dry-oil tests are ooling mode tests where the wet-bulb temperature of the air supplied to the indoor oil is maintained low enough that no ondensate forms on this oil Duted system means an air onditioner or heat pump that is designed to be permanently installed equipment and delivers onditioned air to the indoor spae through a dut(s). The air onditioner or heat pump may be either a split system or a single-pakaged unit Energy effiieny ratio (EER) means the ratio of the average rate of spae ooling delivered to the average rate of eletrial energy onsumed by the air onditioner or heat pump. These rate quantities must be determined from a single test or, if derived via interpolation, must be tied to a single set of operating onditions. EER is expressed in units of Btu/h W When determined for a duted unit tested without an indoor fan installed, EER must inlude the setion 3.3 and default values for the heat output and power input of a fan motor Heating load fator (HLF) means the ratio having as its numerator the total heating delivered during a yli operating interval onsisting of one ON period and one OFF period. The denominator is the total heating that would be delivered, given the same ambient onditions, if the unit operated ontinuously at its steady-state spae heating apaity for the same total time (ON plus OFF) interval Heating seasonal performane fator (HSPF) means the total spae heating required during the spae heating season, expressed in Btu's, divided by the total eletrial energy onsumed by the heat pump system during the same season, expressed in watt-hours. The HSPF used to evaluate ompliane with the Energy Conservation Standards (see 10 CFR (), Subpart C) is based on Region IV, the minimum standardized design heating requirement, and the sampling plan stated in 10 CFR (m), Subpart B Heat pump having a heat omfort ontroller means equipment that regulates the operation of the eletri resistane elements to assure that the air temperature leaving the indoor setion does not fall below a speified temperature. This speified temperature is usually field adjustable. Heat pumps that atively regulate the rate of eletri resistane heating when operating below the balane point (as the result of a seond stage all from the thermostat) but do not operate to maintain a minimum delivery temperature are not onsidered as having a heat omfort ontroller Mini-split air onditioners and heat pumps means systems that have a single outdoor setion and one or more indoor setions. The indoor setions yle on and off in unison in response to a single indoor thermostat Multiple-split air onditioners and heat pumps means systems that have two or more indoor setions. The indoor setions operate independently and an be used to ondition multiple zones in response to multiple indoor thermostats Non-duted system means an air onditioner or heat pump that is designed to be permanently installed equipment and diretly heats or ools air within the onditioned spae using one or more indoor oils that are mounted on room walls and/or eilings. The unit may be of a modular design that allows for ombining multiple outdoor oils and ompressors to reate one overall system. Non-duted systems overed by this test proedure are all split systems. 41

49 ANSI/AHRI STANDARD 210/ Part-load fator (PLF) means the ratio of the yli energy effiieny ratio (oeffiient of performane) to the steadystate energy effiieny ratio (oeffiient of performane). Evaluate both energy effiieny ratios (oeffiients of performane) based on operation at the same ambient onditions Seasonal energy effiieny ratio (SEER) means the total heat removed from the onditioned spae during the annual ooling season, expressed in Btu's, divided by the total eletrial energy onsumed by the air onditioner or heat pump during the same season, expressed in watt-hours. The SEER alulation in setion 4.1 of this Appendix and the sampling plan stated in 10 CFR Subpart B, (m) are used to evaluate ompliane with the Energy Conservation Standards. (See 10 CFR (), Subpart C.) 1.34 Single-pakaged unit means any entral air onditioner or heat pump that has all major assemblies enlosed in one abinet Small-dut, high-veloity system means a system that ontains a blower and indoor oil ombination that is designed for, and produes, at least 1.2 inhes (of water) of external stati pressure when operated at the full-load air volume rate of fm per rated ton of ooling. When applied in the field, small-dut produts use high-veloity room outlets (i.e., generally greater than 1000 fpm) having less than 6.0 square inhes of free area Split system means any air onditioner or heat pump that has one or more of the major assemblies separated from the others Standard air means dry air having a mass density of lb/ft Steady-state test means a test where the test onditions are regulated to remain as onstant as possible while the unit operates ontinuously in the same mode Temperature bin means the 5 F inrements that are used to partition the outdoor dry-bulb temperature ranges of the ooling ( 65 F) and heating (<65 F) seasons Test ondition tolerane means the maximum permissible differene between the average value of the measured test parameter and the speified test ondition Test operating tolerane means the maximum permissible range that a measurement may vary over the speified test interval. The differene between the maximum and minimum sampled values must be less than or equal to the speified test operating tolerane Time adaptive defrost ontrol system is a demand-defrost ontrol system (see definition 1.21) that measures the length of the prior defrost period(s) and uses that information to automatially determine when to initiate the next defrost yle Time-temperature defrost ontrol systems initiate or evaluate initiating a defrost yle only when a predetermined umulative ompressor ON-time is obtained. This predetermined ON-time is generally a fixed value (e.g., 30, 45, 90 minutes) although it may vary based on the measured outdoor dry-bulb temperature. The ON-time ounter aumulates if ontroller measurements (e.g., outdoor temperature, evaporator temperature) indiate that frost formation onditions are present, and it is reset/remains at zero at all other times. In one appliation of the ontrol sheme, a defrost is initiated whenever the ounter time equals the predetermined ON-time. The ounter is reset when the defrost yle is ompleted. In a seond appliation of the ontrol sheme, one or more parameters are measured (e.g., air and/or refrigerant temperatures) at the predetermined, umulative, ompressor ON-time. A defrost is initiated only if the measured parameter(s) falls within a predetermined range. The ON-time ounter is reset regardless of whether a defrost is initiated. If systems of this seond type use umulative ON-time intervals of 10 minutes or less, then the heat pump may qualify as having a demand defrost ontrol system (see definition 1.21) Triple-split system means an air onditioner or heat pump that is omposed of three separate omponents: An outdoor fan oil setion, an indoor fan oil setion, and an indoor ompressor setion Two-apaity (or two-stage) ompressor means an air onditioner or heat pump that has one of the following: 42

50 ANSI/AHRI STANDARD 210/ (1) A two-speed ompressor, (2) Two ompressors where only one ompressor ever operates at a time, (3) Two ompressors where one ompressor (Compressor #1) operates at low loads and both ompressors (Compressors #1 and #2) operate at high loads but Compressor #2 never operates alone, or (4) A ompressor that is apable of ylinder or sroll unloading. For suh systems, low apaity means: (1) Operating at low ompressor speed, (2) Operating the lower apaity ompressor, (3) Operating Compressor #1, or (4) Operating with the ompressor unloaded (e.g., operating one piston of a two-piston reiproating ompressor, using a fixed frational volume of the full sroll, et.). For suh systems, high apaity means: (1) Operating at high ompressor speed, (2) Operating the higher apaity ompressor, (3) Operating Compressors #1 and #2, or (4) Operating with the ompressor loaded (e.g., operating both pistons of a two-piston reiproating ompressor, using the full volume of the sroll) Two-apaity, northern heat pump means a heat pump that has a fatory or field-seletable lok-out feature to prevent spae ooling at high-apaity. Two-apaity heat pumps having this feature will typially have two sets of ratings, one with the feature disabled and one with the feature enabled. The indoor oil model number should reflet whether the ratings pertain to the lokout enabled option via the inlusion of an extra identifier, suh as +LO. When testing as a two-apaity, northern heat pump, the lokout feature must remain enabled for all tests Wet-oil test means a test onduted at test onditions that typially ause water vapor to ondense on the test unit evaporator oil. 2. Testing Conditions This test proedure overs split-type and single-pakaged duted units and split-type non-duted units. Exept for units having a variable-speed ompressor, duted units tested without an indoor fan installed are overed. a. Only a subset of the setions listed in this test proedure apply when testing and rating a partiular unit. Tables 1 A through 1 C show whih setions of the test proedure apply to eah type of equipment. In eah table, look at all four of the Roman numeral ategories to see what test setions apply to the equipment being tested. 1. The first ategory, Rows I 1 through I 4 of the Tables, pertains to the ompressor and indoor fan features of the equipment. After identifying the orret I row, find the table ells in the same row that list the type of equipment being tested: Air onditioner (), heat pump (), or heating-only heat pump (). Use the test setion(s) listed above eah noted table ell for testing and rating the unit. 43

51 ANSI/AHRI STANDARD 210/ The seond ategory, Rows II 1 and II 2, pertains to the presene or absene of duts. Row II 1 shows the test proedure setions that apply to duted systems, and Row II 2 shows those that apply to non-duted systems. 3. The third ategory is for speial features that may be present in the equipment. When testing units that have one or more of the three (speial) equipment features desribed by the Table legend for Category III, use Row III to find test setions that apply. 4. The fourth ategory is for the seondary test method to be used. If the seondary method for determining the unit's ooling and/or heating apaity is known, use Row IV to find the appropriate test setions. Otherwise, inlude all of the test setions referened by Row IV ell entries i.e., setions 2.10 to and 3.11 to among those setions onsulted for testing and rating information. b. Obtain a omplete listing of all pertinent test setions by reording those setions identified from the four ategories above.. The user should note that, for many setions, only part of a setion applies to the unit being tested. In a few ases, the entire setion may not apply. For example, setions 3.4 to (whih desribe optional dry oil tests), are not relevant if the allowed default value for the ooling mode yli degradation oeffiient is used rather than determining it by testing. Example for Using Tables 1 A to 1 C Equipment Desription: A duted air onditioner having a single-speed ompressor, a fixed-speed indoor fan, and a multispeed outdoor fan. Seondary Test Method: Refrigerant Enthalpy Method Step 1. Determine whih of four listed Row I options applies ==> Row I 2 Table 1 A: in Row I 2 is found in the olumns for setions 1.1 to 1.47, 2.1 to 2.2, to , 2.2.5, 2.3 to 2.3.1, 2.4 to 2.4.1, 2.5, to 2.10, and 2.11 to Table 1 B: is listed in Row I 2 for setions 3 to 3.1.4, to 3.1.8, 3.2.1, 3.3 to 3.5, 3.5.3, 3.11 and Table 1 C: is listed in Row I 2 for setions and 4.4. Step 2. Equipment is duted ==> Row II 1 Table 1 A: is listed in Row II 1 for setions and to Table 1 B: is listed in Row II 1 for setions to and Table 1 C: no listings in Row II 1. Step 3. Equipment Speial Features inlude multi-speed outdoor fan ==> Row III, M Table 1 A: M is listed in Row III for setion Tables 1 B and 1 C: no M listings in Row III. 44

52 ANSI/AHRI STANDARD 210/ Step 4. Seondary Test Method is Refrigerant Enthalpy Method ==> Row IV, R Table 1 A: R is listed in Row IV for setion Table 1 B: R is listed in Row IV for setion Table 1 C: no R listings in Row IV. Step 5. Cumulative listing of appliable test proedure setions 1.1 to 1.47, 2.1 to 2.2, 2.2.2, to 2.4.1, 2.2.5, 2.3 to 2.3.1, 2.4 to 2.4.1, 2.4.2, 2.5, to , to 2.10, , 2.11 to 2.13, 3. to 3.1.4, to , to 3.1.8, 3.2.1, 3.3 to 3.5, 3.5.1, 3.5.3, 3.11, , 3.12, 4.1.1, and

53 46 Key Equipment Features and Seondary Test Method Table 1A. Seletion of Test Proedure Setions: Setion 1 (Definitions) and Setion 2 (Testing Conditions) Setions From the Test Proedure I-1. Single-speed Compressor; Variablespeed Variable Air Volume Rate Indoor Fan I-2. Single-speed Compressor Exept as Covered by I-1 I-3. Two-apaity Compressor I-4. Variable-speed Compressor II-1. Duted II-2. Non-Duted 1.1 to to III. Speial Features M G Legend for Table Entries Categories I and II: = applies for an Air Conditioner that meets the orresponding Column 1 Key Equipment... riterion = applies for a Heat Pump that meets the orresponding Column 1 Key Equipment... riterion = applies for a Heating-only Heat Pump that meets the orresponding Column 1 Key Equipment... riterion Category III: G = ganged mini-splits or multi-splits; H = heat pump with a heat omfort ontroller; M = units with a multi-speed outdoor fan. Category IV: O = Outdoor Air Enthalpy Method; C = Compressor Calibration Method; R = Refrigerant Enthalpy Method IV. Seondary Test Method O C R to to to to to to 2.13 ANSI/AHRI STANDARD 210/

54 47 Key Equipment Features and Seondary Test Method Setions From the Test Proedure I-1. Single-speed Compressor; Variablespeed Variable Air Volume Rate Indoor Fan I-2. Single-speed Compressor Exept as Covered by I-1 I-3. Two-apaity Compressor I-4. Variable-speed Compressor II-1. Duted II-2. Non-Duted III. Speial Features IV. Seondary Test Method Table 1B. Seletion of Test Proedure Setions: Setion 3 (Testing Proedures) 3. to to Legend for Table Entries Categories I and II: = applies for an Air Conditioner that meets the orresponding Column 1 Key Equipment... riterion = applies for a Heat Pump that meets the orresponding Column 1 Key Equipment... riterion = applies for a Heating-only Heat Pump that meets the orresponding Column 1 Key Equipment... riterion Category III: G = ganged mini-splits or multi-splits; H = heat pump with a heat omfort ontroller; M = units with a multi-speed outdoor fan. Category IV: O = Outdoor Air Enthalpy Method; C = Compressor Calibration Method; R = Refrigerant Enthalpy Method to to to H to to ANSI/AHRI STANDARD 210/

55 48 Key Equipment Features and Seondary Test Method Table 1B. Seletion of Test Proedure Setions: Setion 3 (Testing Proedures) (ontinued) Setions From the Test Proedure I-1. Single-speed Compressor; Variablespeed Variable Air Volume Rate Indoor Fan I-2. Single-speed Compressor Exept as Covered by I-1 I-3. Two-apaity Compressor I-4. Variable-speed Compressor II-1. Duted II-2. Non-Duted III. Speial Features H IV. Seondary Test Method O C R Legend for Table Entries Categories I and II: = applies for an Air Conditioner that meets the orresponding Column 1 Key Equipment... riterion = applies for a Heat Pump that meets the orresponding Column 1 Key Equipment... riterion = applies for a Heating-only Heat Pump that meets the orresponding Column 1 Key Equipment... riterion Category III: G = ganged mini-splits or multi-splits; H = heat pump with a heat omfort ontroller; M = units with a multi-speed outdoor fan. Category IV: O = Outdoor Air Enthalpy Method; C = Compressor Calibration Method; R = Refrigerant Enthalpy Method to to to ANSI/AHRI STANDARD 210/

56 49 Table 1C. Seletion of Test Proedure Setions: Setion 4 (Calulations of Seasonal Performane Desriptors) Key Equipment Features and Seondary Test Method Setions From the Test Proedure I-1. Single-speed Compressor; Variable-speed Variable Air Volume Rate Indoor Fan I-2. Single-speed Compressor Exept as Covered by I-1 I-3. Two-apaity Compressor I-4. Variable-speed Compressor II-1. Duted 4 to 4.1 II-2. Non-Duted III. Speial Features H H IV. Seondary Test Method Legend for Table Entries Categories I and II: = applies for an Air Conditioner that meets the orresponding Column 1 Key Equipment... riterion = applies for a Heat Pump that meets the orresponding Column 1 Key Equipment... riterion = applies for a Heating-only Heat Pump that meets the orresponding Column 1 Key Equipment... riterion Category III: G = ganged mini-splits or multi-splits; H = heat pump with a heat omfort ontroller; M = units with a multi-speed outdoor fan. Category IV: O = Outdoor Air Enthalpy Method; C = Compressor Calibration Method; R = Refrigerant Enthalpy Method to to to to to to to ANSI/AHRI STANDARD 210/

57 ANSI/AHRI STANDARD 210/ Test room requirements. a. Test using two side-by-side rooms, an indoor test room and an outdoor test room. For multiple-split air onditioners and heat pumps (see Definition 1.30), however, use as many available indoor test rooms as needed to aommodate the total number of indoor units. These rooms must omply with the requirements speified in setions and of ASHRAE Standard (inorporated by referene, see ). b. Inside these test rooms, use artifiial loads during yli tests and frost aumulation tests, if needed, to produe stabilized room air temperatures. For one room, selet an eletri resistane heater(s) having a heating apaity that is approximately equal to the heating apaity of the test unit's ondenser. For the seond room, selet a heater(s) having a apaity that is lose to the sensible ooling apaity of the test unit's evaporator. When applied, yle the heater loated in the same room as the test unit evaporator oil ON and OFF when the test unit yles ON and OFF. Cyle the heater loated in the same room as the test unit ondensing oil ON and OFF when the test unit yles OFF and ON. 2.2 Test unit installation requirements. a. Install the unit aording to setion 8.2 of ASHRAE Standard (inorporated by referene, see ). With respet to interonneting tubing used when testing split-systems, however, follow the requirements given in setion of AHRI Standard 210/ (inorporated by referene, see ). When testing triple-split systems (see Definition 1.44), use the tubing length speified in setion of AHRI Standard 210/ (inorporated by referene, see ) to onnet the outdoor oil, indoor ompressor setion, and indoor oil while still meeting the requirement of exposing 10 feet of the tubing to outside onditions. When testing split systems having multiple indoor oils, onnet eah indoor fan-oil to the outdoor unit using: (a) 25 feet of tubing, or (b) tubing furnished by the manufaturer, whihever is longer. If they are needed to make a seondary measurement of apaity, install refrigerant pressure measuring instruments as desribed in setion of ASHRAE Standard (inorporated by referene, see ). Refer to setion 2.10 of this Appendix to learn whih seondary methods require refrigerant pressure measurements. At a minimum, insulate the low-pressure line(s) of a split-system with insulation having an inside diameter that mathes the refrigerant tubing and a nominal thikness of 0.5 inh. b. For units designed for both horizontal and vertial installation or for both up-flow and down-flow vertial installations, the manufaturer must speify the orientation used for testing. Condut testing with the following installed: (1) the most restritive filter(s); (2) supplementary heating oils; and (3) other equipment speified as part of the unit, inluding all hardware used by a heat omfort ontroller if so equipped (see Definition 1.28). For small-dut, high-veloity systems, onfigure all balane dampers or restritor devies on or inside the unit to fully open or lowest restrition.. Testing a duted unit without having an indoor air filter installed is permissible as long as the minimum external stati pressure requirement is adjusted as stated in Table 2, note 3 (see setion 3.1.4). Exept as noted in setion 3.1.9, prevent the indoor air supplementary heating oils from operating during all tests. For oil-only indoor units that are supplied without an enlosure, reate an enlosure using 1 inh fiberglass dutboard having a nominal density of 6 pounds per ubi foot. Or alternatively, use some other insulating material having a thermal resistane ( R value) between 4 and 6 hr ft 2 F/Btu. For units where the oil is housed within an enlosure or abinet, no extra insulating or sealing is allowed Defrost ontrol settings. Set heat pump defrost ontrols at the normal settings whih most typify those enountered in generalized limati region IV. (Refer to Figure 2 and Table 17 of setion 4.2 for information on region IV.) For heat pumps that use a time-adaptive defrost ontrol system (see Definition 1.42), the manufaturer must speify the frosting interval to be used during Frost Aumulation tests and provide the proedure for manually initiating the defrost at the speified time. To ease testing of any unit, the manufaturer should provide information and any neessary hardware to manually initiate a defrost yle Speial requirements for units having a multiple-speed outdoor fan. Configure the multiple-speed outdoor fan aording to the manufaturer's speifiations, and thereafter, leave it unhanged for all tests. The ontrols of the unit must regulate the operation of the outdoor fan during all lab tests exept dry oil ooling mode tests. For dry oil ooling mode tests, the outdoor fan must operate at the same speed used during the required wet oil test onduted at the same outdoor test onditions Speial requirements for multi-split air onditioners and heat pumps, and systems omposed of multiple mini-split units (outdoor units loated side-by-side) that would normally operate using two or more indoor thermostats. For any test 47

58 ANSI/ANSI/AHRI STANDARD 210/ where the system is operated at part load (i.e., one or more ompressors off, operating at the intermediate or minimum ompressor speed, or at low ompressor apaity), the manufaturer shall designate the partiular indoor oils that are turned off during the test. For variable-speed systems, the manufaturer must designate at least one indoor unit that is turned off for all tests onduted at minimum ompressor speed. For all other part-load tests, the manufaturer shall hoose to turn off zero, one, two, or more indoor units. The hosen onfiguration shall remain unhanged for all tests onduted at the same ompressor speed/apaity. For any indoor oil that is turned off during a test, take steps to ease fored airflow through this indoor oil and blok its outlet dut. Beause these types of systems will have more than one indoor fan and possibly multiple outdoor fans and ompressor systems, referenes in this test proedure to a single indoor fan, outdoor fan, and ompressor means all indoor fans, all outdoor fans, and all ompressor systems that are turned on during the test Wet-bulb temperature requirements for the air entering the indoor and outdoor oils Cooling mode tests. For wet-oil ooling mode tests, regulate the water vapor ontent of the air entering the indoor unit to the appliable wet-bulb temperature listed in Tables 3 to 6. As noted in these same tables, ahieve a wet-bulb temperature during dry-oil ooling mode tests that results in no ondensate forming on the indoor oil. Controlling the water vapor ontent of the air entering the outdoor side of the unit is not required for ooling mode tests exept when testing: (1) Units that rejet ondensate to the outdoor oil during wet oil tests. Tables 3 6 list the appliable wet-bulb temperatures. (2) Single-pakaged units where all or part of the indoor setion is loated in the outdoor test room. The average dew point temperature of the air entering the outdoor oil during wet oil tests must be within ±3.0 F of the average dew point temperature of the air entering the indoor oil over the 30-minute data olletion interval desribed in setion 3.3. For dry oil tests on suh units, it may be neessary to limit the moisture ontent of the air entering the outdoor side of the unit to meet the requirements of setion Heating mode tests. For heating mode tests, regulate the water vapor ontent of the air entering the outdoor unit to the appliable wet-bulb temperature listed in Tables 9 to 12. The wet-bulb temperature entering the indoor side of the heat pump must not exeed 60 F. Additionally, if the Outdoor Air Enthalpy test method is used while testing a single-pakaged heat pump where all or part of the outdoor setion is loated in the indoor test room, adjust the wet-bulb temperature for the air entering the indoor side to yield an indoor-side dew point temperature that is as lose as reasonably possible to the dew point temperature of the outdoor-side entering air Additional refrigerant harging requirements. Charging aording to the manufaturer s published instrutions, as stated in setion 8.2 of ASHRAE Standard (inorporated by referene, see ), means the manufaturer s installation instrutions that ome pakaged with the unit. 2.3 Indoor air volume rates. If a unit's ontrols allow for overspeeding the indoor fan (usually on a temporary basis), take the neessary steps to prevent overspeeding during all tests Cooling tests. a. Set indoor fan ontrol options (e.g., fan motor pin settings, fan motor speed) aording to the published installation instrutions that are provided with the equipment while meeting the airflow requirements that are speified in setions to b. Express the Cooling Full-load Air Volume Rate, the Cooling Minimum Air Volume Rate, and the Cooling Intermediate Air Volume Rate in terms of standard air Heating tests. a. If needed, set the indoor fan ontrol options (e.g., fan motor pin settings, fan motor speed) aording to the published installation instrutions that are provided with the equipment. Do this set-up while meeting all appliable airflow requirements speified in setions to b. Express the Heating Full-load Air Volume Rate, the Heating Minimum Air Volume Rate, the Heating Intermediate Air Volume Rate, and the Heating Nominal Air Volume Rate in terms of standard air. 2.4 Indoor oil inlet and outlet dut onnetions. Insulate and/or onstrut the outlet plenum desribed in setion and, if installed, the inlet plenum desribed in setion with thermal insulation having a nominal overall resistane (R-value) of at least 19 hr ft 2 F/Btu Outlet plenum for the indoor unit. a. Attah a plenum to the outlet of the indoor oil. (Note: for some pakaged systems, the indoor oil may be loated in the outdoor test room.) 48

59 ANSI/AHRI STANDARD 210/ b. For systems having multiple indoor oils, attah a plenum to eah indoor oil outlet. Connet two or more outlet plenums to a single ommon dut so that eah indoor oil ultimately onnets to an airflow measuring apparatus (setion 2.6). If using more than one indoor test room, do likewise, reating one or more ommon duts within eah test room that ontains multiple indoor oils. At the plane where eah plenum enters a ommon dut, install an adjustable airflow damper and use it to equalize the stati pressure in eah plenum. Eah outlet air temperature grid (setion 2.5.4) and airflow measuring apparatus are loated downstream of the inlet(s) to the ommon dut.. For small-dut, high-veloity systems, install an outlet plenum that has a diameter that is equal to or less than the value listed below. The limit depends only on the ooling Full-load Air Volume Rate (see setion ) and is effetive regardless of the flange dimensions on the outlet of the unit (or an air supply plenum adapter aessory, if installed in aordane with the manufaturers installation instrutions). d. Add a stati pressure tap to eah fae of the (eah) outlet plenum, if retangular, or at four evenly distributed loations along the irumferene of an oval or round plenum. Create a manifold that onnets the four stati pressure taps. Figure 1 shows two of the three options allowed for the manifold onfiguration; the third option is the broken-ring, four-to-one manifold onfiguration that is shown in Figure 7a of ASHRAE Standard (inorporated by referene, see ). See Figures 7a, 7b, 7, and 8 of ASHRAE Standard (inorporated by referene, see ) for the ross-setional dimensions and minimum length of the (eah) plenum and the loations for adding the stati pressure taps for units tested with and without an indoor fan installed. Cooling Full-Load Air Volume Rate Maximum Diameter* of Outlet Plenum (sfm) (inhes) to to to to to *If the outlet plenum is retangular, alulate its equivalent diameter using (4A)/P, where A is the area and P is the perimeter of the retangular plenum, and ompare it to the listed maximum diameter. 49

60 ANSI/ANSI/AHRI STANDARD 210/ Figure 1. Configurations for manifolding the stati pressure taps. The top two diagrams show the omplete ring, four-to-one onfiguration. The lower two diagrams show the trip-t onfiguration Inlet plenum for the indoor unit. Install an inlet plenum when testing a oil-only indoor unit or a pakaged system where the indoor oil is loated in the outdoor test room. Add stati pressure taps at the enter of eah fae of this plenum, if retangular, or at four evenly distributed loations along the irumferene of an oval or round plenum. Make a manifold that onnets the four stati-pressure taps using one of the three onfigurations speified in setion See Figures 7b, 7, and Figure 8 of ASHRAE Standard (inorporated by referene, see ) for ross-setional dimensions, the minimum length of the inlet plenum, and the loations of the stati-pressure taps. When testing a duted unit having an indoor fan (and the indoor oil is in the indoor test room), the manufaturer has the option to test with or without an inlet plenum installed. Spae limitations within the test room may ditate that the manufaturer hoose the latter option. If used, onstrut the inlet plenum and add the four stati-pressure taps as shown in Figure 8 of ASHRAE Standard (inorporated by referene, see ). Manifold the four stati-pressure taps using one of the three onfigurations speified in setion Never use an inlet plenum when testing a non-duted system. 2.5 Indoor oil air property measurements and air damper box appliations. a. Measure the dry-bulb temperature and water vapor ontent of the air entering and leaving the indoor oil. If needed, use an air sampling devie to divert air to a sensor(s) that measures the water vapor ontent of the air. See Figure 2 of ASHRAE Standard (RA 01) (inorporated by referene, see ) for guidane on onstruting an air sampling devie. The sampling devie may also divert air to a remotely loated sensor(s) that measures dry bulb temperature. The air sampling devie and the remotely loated temperature sensor(s) may be used to determine the entering air dry bulb temperature during any test. The air sampling devie and the remotely loated leaving air dry bulb temperature sensor(s) may be used for all tests exept: 50

61 ANSI/AHRI STANDARD 210/ (1) Cyli tests; and (2) Frost aumulation tests. b. An aeptable alternative in all ases, inluding the two speial ases noted above, is to install a grid of dry bulb temperature sensors within the outlet and inlet duts. Use a temperature grid to get the average dry bulb temperature at one loation, leaving or entering, or when two grids are applied as a thermopile, to diretly obtain the temperature differene. A grid of temperature sensors (whih may also be used for determining average leaving air dry bulb temperature) is required to measure the temperature distribution within a ross-setion of the leaving airstream.. Use an inlet and outlet air damper box when testing duted systems if onduting one or both of the yli tests listed in setions 3.2 and 3.6. Otherwise, install an outlet air damper box when testing heat pumps, both duted and non-duted, that yle off the indoor fan during defrost yles if no other means is available for preventing natural or fored onvetion through the indoor unit when the indoor fan is off. Never use an inlet damper box when testing a non-duted system Test set-up on the inlet side of the indoor oil: for ases where the inlet damper box is installed. a. Install the inlet side damper box as speified in setion or , whihever applies. Insulate or onstrut the dutwork between the point where the air damper is installed and where the onnetion is made to either the inlet plenum (setion units) or the indoor unit (setion units) with thermal insulation that has a nominal overall resistane (R-value) of at least 19 hr ft 2 F/Btu. b. Loate the grid of entering air dry-bulb temperature sensors, if used, at the inlet of the damper box. Loate the air sampling devie, or the sensor used to measure the water vapor ontent of the inlet air, at a loation immediately upstream of the damper box inlet If the setion inlet plenum is installed. Install the inlet damper box upstream of the inlet plenum. The rosssetional flow area of the damper box must be equal to or greater than the flow area of the inlet plenum. If needed, use an adaptor plate or a transition dut setion to onnet the damper box with the inlet plenum If the setion inlet plenum is not installed. Install the damper box immediately upstream of the air inlet of the indoor unit. The ross-setional dimensions of the damper box must be equal to or greater than the dimensions of the indoor unit inlet. If needed, use an adaptor plate or a short transition dut setion to onnet the damper box with the unit's air inlet. Add stati pressure taps at the enter of eah fae of the damper box, if retangular, or at four evenly distributed loations along the irumferene, if oval or round. Loate the pressure taps between the inlet damper and the inlet of the indoor unit. Make a manifold that onnets the four stati pressure taps Test set-up on the inlet side of the indoor unit: for ases where no inlet damper box is installed. If using the setion inlet plenum and a grid of dry bulb temperature sensors, mount the grid at a loation upstream of the stati pressure taps desribed in setion 2.4.2, preferably at the entrane plane of the inlet plenum. If the setion inlet plenum is not used, but a grid of dry bulb temperature sensors is used, loate the grid approximately 6 inhes upstream from the inlet of the indoor oil. Or, in the ase of non-duted units having multiple indoor oils, loate a grid approximately 6 inhes upstream from the inlet of eah indoor oil. Position an air sampling devie, or the sensor used to measure the water vapor ontent of the inlet air, immediately upstream of the (eah) entering air dry-bulb temperature sensor grid. If a grid of sensors is not used, position the entering air sampling devie (or the sensor used to measure the water vapor ontent of the inlet air) as if the grid were present Indoor oil stati pressure differene measurement. Setion of ASHRAE Standard (inorporated by referene, see ) desribes the method for fabriating stati pressure taps. Also refer to Figure 2A of ASHRAE Standard 51 99/AMCA Standard (inorporated by referene, see ). Use a differential pressure measuring instrument that is aurate to within ±0.01 inhes of water and has a resolution of at least 0.01 inhes of water to measure the stati pressure differene between the indoor oil air inlet and outlet. Connet one side of the differential pressure instrument to the manifolded pressure taps installed in the outlet plenum. Connet the other side of the instrument to the manifolded pressure taps loated in either the inlet plenum or inorporated within the air damper box. If an inlet plenum or inlet damper box are not used, leave the inlet side of the differential pressure instrument open to the surrounding atmosphere. For nonduted systems that are tested with multiple outlet plenums, measure the stati pressure within eah outlet plenum relative to the surrounding atmosphere. 51

62 ANSI/ANSI/AHRI STANDARD 210/ Test set-up on the outlet side of the indoor oil. a. Install an interonneting dut between the outlet plenum desribed in setion and the airflow measuring apparatus desribed below in setion 2.6. The ross-setional flow area of the interonneting dut must be equal to or greater than the flow area of the outlet plenum or the ommon dut used when testing non-duted units having multiple indoor oils. If needed, use adaptor plates or transition dut setions to allow the onnetions. To minimize leakage, tape joints within the interonneting dut (and the outlet plenum). Construt or insulate the entire flow setion with thermal insulation having a nominal overall resistane (R-value) of at least 19 hr ft 2 F/Btu. b. Install a grid(s) of dry-bulb temperature sensors inside the interonneting dut. Also, install an air sampling devie, or the sensor(s) used to measure the water vapor ontent of the outlet air, inside the interonneting dut. Loate the dry-bulb temperature grid(s) upstream of the air sampling devie (or the in-dut sensor(s) used to measure the water vapor ontent of the outlet air). Air that irulates through an air sampling devie and past a remote water-vapor-ontent sensor(s) must be returned to the interonneting dut at a point: (1) Downstream of the air sampling devie; (2) Upstream of the outlet air damper box, if installed; and (3) Upstream of the setion 2.6 airflow measuring apparatus Outlet air damper box plaement and requirements. If using an outlet air damper box (see setion 2.5), install it within the interonneting dut at a loation downstream of the loation where air from the sampling devie is reintrodued or downstream of the in-dut sensor that measures water vapor ontent of the outlet air. The leakage rate from the ombination of the outlet plenum, the losed damper, and the dut setion that onnets these two omponents must not exeed 20 ubi feet per minute when a negative pressure of 1 inh of water olumn is maintained at the plenum's inlet Proedures to minimize temperature maldistribution. Use these proedures if neessary to orret temperature maldistributions. Install a mixing devie(s) upstream of the outlet air, dry-bulb temperature grid (but downstream of the outlet plenum stati pressure taps). Use a perforated sreen loated between the mixing devie and the dry-bulb temperature grid, with a maximum open area of 40 perent. One or both items should help to meet the maximum outlet air temperature distribution speified in setion Mixing devies are desribed in setions of ASHRAE Standard (RA 01) (inorporated by referene, see ) and setion of ASHRAE Standard (RA 92) (inorporated by referene, see ) Minimizing air leakage. For small-dut, high-veloity systems, install an air damper near the end of the interonneting dut, just prior to the transition to the airflow measuring apparatus of setion 2.6. To minimize air leakage, adjust this damper suh that the pressure in the reeiving hamber of the airflow measuring apparatus is no more than 0.5 inh of water higher than the surrounding test room ambient. In lieu of installing a separate damper, use the outlet air damper box of setions 2.5 and if it allows variable positioning. Also apply these steps to any onventional indoor blower unit that reates a stati pressure within the reeiving hamber of the airflow measuring apparatus that exeeds the test room ambient pressure by more than 0.5 inhes of water olumn Dry bulb temperature measurement. a. Measure dry bulb temperatures as speified in setions 4, 5, , 9, 10, and 11 of ASHRAE Standard (RA 01) (inorporated by referene, see ). The transient testing requirements ited in setion 4.3 of ASHRAE Standard (RA 01) (inorporated by referene, see ) apply if onduting a yli or frost aumulation test. b. Distribute the sensors of a dry-bulb temperature grid over the entire flow area. The required minimum is 9 sensors per grid Water vapor ontent measurement. Determine water vapor ontent by measuring dry-bulb temperature ombined with the air wet-bulb temperature, dew point temperature, or relative humidity. If used, onstrut and apply wet-bulb temperature sensors as speified in setions 4, 5, 6, 9, 10, and 11 of ASHRAE Standard (RA 01) (inorporated by referene, see ). As speified in ASHRAE (RA 01) (inorporated by referene, see ), the temperature sensor (wik removed) must be aurate to within ±0.2 F. If used, apply dew point hygrometers as speified in setions 5 and 8 of ASHRAE Standard (RA 01) (inorporated by referene, see ). The dew point hygrometers must be aurate to within ±0.4 F when operated at onditions that result in the evaluation of dew points above 35 F. If used, a relative humidity (RH) meter must be aurate to within ±0.7% RH. Other means to determine the psyhrometri state of air may be used as long as the measurement auray is equivalent to or better than the auray ahieved from using a wet-bulb temperature sensor that meets the above speifiations. 52

63 ANSI/AHRI STANDARD 210/ Air damper box performane requirements. If used (see setion 2.5), the air damper box(es) must be apable of being ompletely opened or ompletely losed within 10 seonds for eah ation. 2.6 Airflow measuring apparatus. a. Fabriate and operate an Air Flow Measuring Apparatus as speified in setion 6.6 of ASHRAE Standard (RA05) (inorporated by referene, see ). Refer to Figure 12 of ASHRAE Standard 51 99/AMCA Standard (inorporated by referene, see ) or Figure 14 of ASHRAE Standard (RA 92) (inorporated by referene, see ) for guidane on plaing the stati pressure taps and positioning the diffusion baffle (settling means) relative to the hamber inlet. b. Connet the airflow measuring apparatus to the interonneting dut setion desribed in setion See setions 6.1.1, 6.1.2, and 6.1.4, and Figures 1, 2, and 4 of ASHRAE Standard (inorporated by referene, see ), and Figures D1, D2, and D4 of AHRI Standard 210/ (inorporated by referene, see ) for illustrative examples of how the test apparatus may be applied within a omplete laboratory set-up. Instead of following one of these examples, an alternative set-up may be used to handle the air leaving the airflow measuring apparatus and to supply properly onditioned air to the test unit's inlet. The alternative set-up, however, must not interfere with the presribed means for measuring airflow rate, inlet and outlet air temperatures, inlet and outlet water vapor ontents, and external stati pressures, nor reate abnormal onditions surrounding the test unit. (Note: Do not use an enlosure as desribed in setion of ASHRAE Standard (inorporated by referene, see ) when testing triple-split units.) 2.7 Eletrial voltage supply. Perform all tests at the voltage speified in setion of AHRI Standard 210/ (inorporated by referene, see ) for Standard Rating Tests. Measure the supply voltage at the terminals on the test unit using a volt meter that provides a reading that is aurate to within ±1.0 perent of the measured quantity. 2.8 Eletrial power and energy measurements. a. Use an integrating power (watt-hour) measuring system to determine the eletrial energy or average eletrial power supplied to all omponents of the air onditioner or heat pump (inluding auxiliary omponents suh as ontrols, transformers, rankase heater, integral ondensate pump on non-duted indoor units, et.). The watt-hour measuring system must give readings that are aurate to within ±0.5 perent. For yli tests, this auray is required during both the ON and OFF yles. Use either two different sales on the same watt-hour meter or two separate watt-hour meters. Ativate the sale or meter having the lower power rating within 15 seonds after beginning an OFF yle. Ativate the sale or meter having the higher power rating ative within 15 seonds prior to beginning an ON yle. For duted units tested with a fan installed, the ON yle lasts from ompressor ON to indoor fan OFF. For duted units tested without an indoor fan installed, the ON yle lasts from ompressor ON to ompressor OFF. For non-duted units, the ON yle lasts from indoor fan ON to indoor fan OFF. When testing air onditioners and heat pumps having a variable-speed ompressor, avoid using an indution watt/watt-hour meter. b. When performing setion 3.5 and/or 3.8 yli tests on non-duted units, provide instrumentation to determine the average eletrial power onsumption of the indoor fan motor to within ±1.0 perent. If required aording to setions 3.3, 3.4, 3.7, 3.9.1, and/or 3.10, this same instrumentation requirement applies when testing air onditioners and heat pumps having a variable-speed onstant-air-volume-rate indoor fan or a variable-speed, variable-air-volume-rate indoor fan. 2.9 Time measurements. Make elapsed time measurements using an instrument that yields readings aurate to within ±0.2 perent Test apparatus for the seondary spae onditioning apaity measurement. For all tests, use the Indoor Air Enthalpy Method to measure the unit's apaity. This method uses the test set-up speified in setions 2.4 to 2.6. In addition, for all steady-state tests, ondut a seond, independent measurement of apaity as desribed in setion For split systems, use one of the following seondary measurement methods: Outdoor Air Enthalpy Method, Compressor Calibration Method, or Refrigerant Enthalpy Method. For single pakaged units, use either the Outdoor Air Enthalpy Method or the Compressor Calibration Method as the seondary measurement. 53

64 ANSI/ANSI/AHRI STANDARD 210/ Outdoor Air Enthalpy Method. a. To make a seondary measurement of indoor spae onditioning apaity using the Outdoor Air Enthalpy Method, do the following: (1) Measure the eletrial power onsumption of the test unit; (2) Measure the air-side apaity at the outdoor oil; and (3) Apply a heat balane on the refrigerant yle. b. The test apparatus required for the Outdoor Air Enthalpy Method is a subset of the apparatus used for the Indoor Air Enthalpy Method. Required apparatus inludes the following: (1) An outlet plenum ontaining stati pressure taps (setions 2.4, 2.4.1, and 2.5.3), (2) An airflow measuring apparatus (setion 2.6), (3) A dut setion that onnets these two omponents and itself ontains the instrumentation for measuring the dry-bulb temperature and water vapor ontent of the air leaving the outdoor oil (setions 2.5.4, 2.5.5, and 2.5.6), and (4) On the inlet side, a sampling devie and optional temperature grid (setions 2.5 and 2.5.2).. During the preliminary tests desribed in setions and , measure the evaporator and ondenser temperatures or pressures. On both the outdoor oil and the indoor oil, solder a thermoouple onto a return bend loated at or near the midpoint of eah oil or at points not affeted by vapor superheat or liquid subooling. Alternatively, if the test unit is not sensitive to the refrigerant harge, onnet pressure gages to the aess valves or to ports reated from tapping into the sution and disharge lines. Use this alternative approah when testing a unit harged with a zeotropi refrigerant having a temperature glide in exess of 1 F at the speified test onditions Compressor Calibration Method. Measure refrigerant pressures and temperatures to determine the evaporator superheat and the enthalpy of the refrigerant that enters and exits the indoor oil. Determine refrigerant flow rate or, when the superheat of the refrigerant leaving the evaporator is less than 5 F, total apaity from separate alibration tests onduted under idential operating onditions. When using this method, install instrumentation, measure refrigerant properties, and adjust the refrigerant harge aording to setion of ASHRAE Standard (inorporated by referene, see ). Use refrigerant temperature and pressure measuring instruments that meet the speifiations given in setions and 5.2 of ASHRAE Standard (inorporated by referene, see ) Refrigerant Enthalpy Method. For this method, alulate spae onditioning apaity by determining the refrigerant enthalpy hange for the indoor oil and diretly measuring the refrigerant flow rate. Use setion of ASHRAE Standard (inorporated by referene, see ) for the requirements for this method, inluding the additional instrumentation requirements, and information on plaing the flow meter and a sight glass. Use refrigerant temperature, pressure, and flow measuring instruments that meet the speifiations given in setions 5.1.1, 5.2, and of ASHRAE Standard (inorporated by referene, see ) Measurement of test room ambient onditions. a. If using a test set-up where air is duted diretly from the onditioning apparatus to the indoor oil inlet (see Figure 2, Loop Air-Enthalpy Test Method Arrangement, of ASHRAE Standard (inorporated by referene, see )), add instrumentation to permit measurement of the indoor test room dry-bulb temperature. b. If the Outdoor Air Enthalpy Method is not used, add instrumentation to measure the dry-bulb temperature and the water vapor ontent of the air entering the outdoor oil. If an air sampling devie is used, onstrut and apply the devie as per setion 6 of ASHRAE Standard (RA 01) (inorporated by referene, see ). Take steps (e.g., add or reposition a lab irulating fan), as needed, to minimize the magnitude of the temperature distribution non-uniformity. Position any fan in the outdoor test room while trying to keep air veloities in the viinity of the test unit below 500 feet per minute.. Measure dry bulb temperatures as speified in setions 4, 5, , 9, 10, and 11 of ASHRAE Standard (RA 01) (inorporated by referene, see ). Measure water vapor ontent as stated above in setion

65 ANSI/AHRI STANDARD 210/ Measurement of indoor fan speed. When required, measure fan speed using a revolution ounter, tahometer, or strobosope that gives readings aurate to within ±1.0 perent Measurement of barometri pressure. Determine the average barometri pressure during eah test. Use an instrument that meets the requirements speified in setion 5.2 of ASHRAE Standard (inorporated by referene, see ). 3. Testing Proedures 3.1 General Requirements. If, during the testing proess, an equipment set-up adjustment is made that would alter the performane of the unit when onduting an already ompleted test, then repeat all tests affeted by the adjustment. For yli tests, instead of maintaining an air volume rate, for eah airflow nozzle, maintain the stati pressure differene or veloity pressure during an ON period at the same pressure differene or veloity pressure as measured during the steadystate test onduted at the same test onditions Primary and seondary test methods. For all tests, use the Indoor Air Enthalpy Method test apparatus to determine the unit's spae onditioning apaity. The proedure and data olleted, however, differ slightly depending upon whether the test is a steady-state test, a yli test, or a frost aumulation test. The following setions desribed these differenes. For all steady-state tests (i.e., the A, A 2, A 1, B, B 2, B 1, C, C 1, EV, F 1, G 1, H0 1, H 1, H1 2, H1 1, HI N, H 3, H3 2, and H3 1 Tests), in addition, use one of the aeptable seondary methods speified in setion 2.10 to determine indoor spae onditioning apaity. Calulate this seondary hek of apaity aording to setion The two apaity measurements must agree to within 6 perent to onstitute a valid test. For this apaity omparison, use the Indoor Air Enthalpy Method apaity that is alulated in setion 7.3 of ASHRAE Standard (inorporated by referene, see ) (and, if testing a oil-only unit, do not make the after-test fan heat adjustments desribed in setion 3.3, 3.4, 3.7, and 3.10 of this Appendix). However, inlude the appropriate setion 3.3 to 3.5 and 3.7 to 3.10 fan heat adjustments within the Indoor Air Enthalpy Method apaities used for the setion 4 seasonal alulations Manufaturer-provided equipment overrides. Where needed, the manufaturer must provide a means for overriding the ontrols of the test unit so that the ompressor(s) operates at the speified speed or apaity and the indoor fan operates at the speified speed or delivers the speified air volume rate Airflow through the outdoor oil. For all tests, meet the requirements given in setion of AHRI Standard 210/ (inorporated by referene, see ) when obtaining the airflow through the outdoor oil Airflow through the indoor oil Cooling Full-load Air Volume Rate Cooling Full-load Air Volume Rate for Duted Units. The manufaturer must speify the Cooling Full-load Air Volume Rate. Use this value as long as the following two requirements are satisfied. First, when onduting the A or A 2 Test (exlusively), the measured air volume rate, when divided by the measured indoor air-side total ooling apaity must not exeed 37.5 ubi feet per minute of standard air (sfm) per 1000 Btu/h. If this ratio is exeeded, redue the air volume rate until this ratio is equaled. Use this redued air volume rate for all tests that all for using the Cooling Full-load Air Volume Rate. The seond requirement is as follows: a. For all duted units tested with an indoor fan installed, exept those having a variable-speed, onstant-airvolume-rate indoor fan. The seond requirement applies exlusively to the A or A 2 Test and is met as follows. (1) Ahieve the Cooling Full-load Air Volume Rate, determined in aordane with the previous paragraph; (2) Measure the external stati pressure; (3) If this pressure is equal to or greater than the appliable minimum external stati pressure ited in Table 2, this seond requirement is satisfied. Use the urrent air volume rate for all tests that require the Cooling Full-load Air Volume Rate. (4) If the Table 2 minimum is not equaled or exeeded, (4a) redue the air volume rate until the appliable Table 2 minimum is equaled or 55

66 ANSI/ANSI/AHRI STANDARD 210/ (4b) until the measured air volume rate equals 95 perent of the air volume rate from step 1, whihever ours first. (5) If the onditions of step 4a our first, this seond requirement is satisfied. Use the step 4a redued air volume rate for all tests that require the Cooling Full-load Air Volume Rate. (6) If the onditions of step 4b our first, make an inremental hange to the set-up of the indoor fan (e.g., next highest fan motor pin setting, next highest fan motor speed) and repeat the evaluation proess beginning at above step 1. If the indoor fan set-up annot be further hanged, redue the air volume rate until the appliable Table 2 minimum is equaled. Use this redued air volume rate for all tests that require the Cooling Full-load Air Volume Rate. Table 2. Minimum External Stati Pressure for Duted Systems Tested with an Indoor Fan Installed Rated Cooling (1) or Heating (2) Minimum External Resistane (3) Capaity (Inhes of Water) (Btu/h) All Other Systems Small-Dut, High-Veloity Systems (4,5) Up Thru 28, ,000 to 42, ,000 and Above (1) For air onditioners and heat pumps, the value ited by the manufaturer in published literature for the unit s apaity when operated at the A or A 2 Test onditions. (2) For heating-only heat pumps, the value the manufaturer ites in published literature for the unit s apaity when operated at the H1 or H1 2 Test onditions. (3) For duted units tested without an air filter installed, inrease the appliable tabular value by 0.08 inh of water. (4) See Definition 1.35 to determine if the equipment qualifies as a small-dut, highveloity system. (5) If a losed-loop, air-enthalpy test apparatus is used on the indoor side, limit the resistane to airflow on the inlet side of the indoor blower oil to a maximum value of 0.1 inh of water. Impose the balane of the airflow resistane on the outlet side of the indoor blower. b. For duted units that are tested with a variable-speed, onstant-air-volume-rate indoor fan installed. For all tests that speify the Cooling Full-load Air Volume Rate, obtain an external stati pressure as lose to (but not less than) the appliable Table 2 value that does not ause instability or an automati shutdown of the indoor blower.. For duted units that are tested without an indoor fan installed. For the A or A 2 Test, (exlusively), the pressure drop aross the indoor oil assembly must not exeed 0.30 inhes of water. If this pressure drop is exeeded, redue the air volume rate until the measured pressure drop equals the speified maximum. Use this redued air volume rate for all tests that require the Cooling Full-load Air Volume Rate Cooling Full-load Air Volume Rate for Non-duted Units. For non-duted units, the Cooling Full-load Air Volume Rate is the air volume rate that results during eah test when the unit is operated at an external stati pressure of zero inhes of water. 56

67 ANSI/AHRI STANDARD 210/ Cooling Minimum Air Volume Rate. a. For duted units that regulate the speed (as opposed to the fm) of the indoor fan, Cooling Minimum Fan Speed Cooling Minimum Air Vol. Rate = Cooling Full-load Air Vol. Rate, A Test Fan Speed 2 where Cooling Minimum Fan Speed orresponds to the fan speed used when operating at low ompressor apaity (twoapaity system), the fan speed used when operating at the minimum ompressor speed (variable-speed system), or the lowest fan speed used when ooling (single-speed ompressor and a variable-speed variable-air-volume-rate indoor fan). For suh systems, obtain the Cooling Minimum Air Volume Rate regardless of the external stati pressure. b. For duted units that regulate the air volume rate provided by the indoor fan, the manufaturer must speify the Cooling Minimum Air Volume Rate. For suh systems, ondut all tests that speify the Cooling Minimum Air Volume Rate (i.e., the A 1, B 1, C 1, F 1, and G 1 Tests) at an external stati pressure that does not ause instability or an automati shutdown of the indoor blower while being as lose to, but not less than, Cooling Minimum Air Volume Rate A 1, B 1, C 1, F 1, & G1 Test Pst = Pst,A 2 Cooling Full- load Air Volume Rate where ΔP st,a2 is the appliable Table 2 minimum external stati pressure that was targeted during the A 2 (and B 2 ) Test.. For duted two-apaity units that are tested without an indoor fan installed, the Cooling Minimum Air Volume Rate is the higher of (1) the rate speified by the manufaturer or (2) 75 perent of the Cooling Full-load Air Volume Rate. During the laboratory tests on a oil-only (fanless) unit, obtain this Cooling Minimum Air Volume Rate regardless of the pressure drop aross the indoor oil assembly. d. For non-duted units, the Cooling Minimum Air Volume Rate is the air volume rate that results during eah test when the unit operates at an external stati pressure of zero inhes of water and at the indoor fan setting used at low ompressor apaity (two-apaity system) or minimum ompressor speed (variable-speed system). For units having a single-speed ompressor and a variable-speed variable-air-volume-rate indoor fan, use the lowest fan setting allowed for ooling Cooling Intermediate Air Volume Rate. a. For duted units that regulate the speed of the indoor fan, 2, E Test Fan Speed V Cooling Intermediate Air Vol. Rate = Cooling Full-load Air Vol. Rate, A Test Fan Speed 2 For suh units, obtain the Cooling Intermediate Air Volume Rate regardless of the external stati pressure. b. For duted units that regulate the air volume rate provided by the indoor fan, the manufaturer must speify the Cooling Intermediate Air Volume Rate. For suh systems, ondut the E V Test at an external stati pressure that does not ause instability or an automati shutdown of the indoor blower while being as lose to, but not less than, Cooling Intermediate Air Volume Rate E V Test ΔP st = ΔP st,a, 2 Cooling Full-load Air Volume Rate where ΔP st,a2 is the appliable Table 2 minimum external stati pressure that was targeted during the A 2 (and B 2 ) Test.. For non-duted units, the Cooling Intermediate Air Volume Rate is the air volume rate that results when the unit operates at an external stati pressure of zero inhes of water and at the fan speed seleted by the ontrols of the unit for the E V Test onditions. 2 57

68 ANSI/ANSI/AHRI STANDARD 210/ Heating Full-load Air Volume Rate Duted heat pumps where the Heating and Cooling Full-load Air Volume Rates are the same. a. Use the Cooling Full-load Air Volume Rate as the Heating Full-load Air Volume Rate for: 1. Duted heat pumps that operate at the same indoor fan speed during both the A (or A 2 ) and the H1 (or H1 2 ) Tests; 2. Duted heat pumps that regulate fan speed to deliver the same onstant air volume rate during both the A (or A 2 ) and the H1 (or H1 2 ) Tests; and 3. Duted heat pumps that are tested without an indoor fan installed (exept two-apaity northern heat pumps that are tested only at low apaity ooling see ). b. For heat pumps that meet the above riteria 1 and 3, no minimum requirements apply to the measured external or internal, respetively, stati pressure. For heat pumps that meet the above riterion 2, test at an external stati pressure that does not ause instability or an automati shutdown of the indoor blower while being as lose to, but not less than, the same Table 2 minimum external stati pressure as was speified for the A (or A 2 ) ooling mode test Duted heat pumps where the Heating and Cooling Full-load Air Volume Rates are different due to indoor fan operation. a. For duted heat pumps that regulate the speed (as opposed to the fm) of the indoor fan, = H1 or H1 Test Fan Speed A or A Test Fan Speed 2 Heating Full-load Air Volume Rate Cooling Full-load Air Volume Rate, 2 For suh heat pumps, obtain the Heating Full-load Air Volume Rate without regard to the external stati pressure. b. For duted heat pumps that regulate the air volume rate delivered by the indoor fan, the manufaturer must speify the Heating Full-load Air Volume Rate. For suh heat pumps, ondut all tests that speify the Heating Full-load Air Volume Rate at an external stati pressure that does not ause instability or an automati shutdown of the indoor blower while being as lose to, but not less than, Heating Full- load P st = Cooling Full- load P st Heating Full- load Air Volume Rate Cooling Full- load Air Volume Rate 2, where the Cooling Full-load ΔP st is the appliable Table 2 minimum external stati pressure that was speified for the A or A 2 Test.. When testing duted, two-apaity northern heat pumps (see Definition 1.46), use the appropriate approah of the above two ases for units that are tested with an indoor fan installed. For oil-only (fanless) northern heat pumps, the Heating Fullload Air Volume Rate is the lesser of the rate speified by the manufaturer or 133 perent of the Cooling Full-load Air Volume Rate. For this latter ase, obtain the Heating Full-load Air Volume Rate regardless of the pressure drop aross the indoor oil assembly Duted heating-only heat pumps. The manufaturer must speify the Heating Full-load Air Volume Rate. a. For all duted heating-only heat pumps tested with an indoor fan installed, exept those having a variable-speed, onstantair-volume-rate indoor fan. Condut the following steps only during the first test, the H1 or H1 2 Test. (1) Ahieve the Heating Full-load Air Volume Rate. (2) Measure the external stati pressure. (3) If this pressure is equal to or greater than the Table 2 minimum external stati pressure that applies given the heating-only heat pump s rated heating apaity, use the urrent air volume rate for all tests that require the Heating Full-load Air Volume Rate. 58

69 ANSI/AHRI STANDARD 210/ (4) If the Table 2 minimum is not equaled or exeeded, (4a) redue the air volume rate until the appliable Table 2 minimum is equaled or (4b) until the measured air volume rate equals 95 perent of the manufaturer-speified Full-load Air Volume Rate, whihever ours first. (5) If the onditions of step 4a ours first, use the step 4a redued air volume rate for all tests that require the Heating Full-load Air Volume Rate. (6) If the onditions of step 4b our first, make an inremental hange to the set-up of the indoor fan (e.g., next highest fan motor pin setting, next highest fan motor speed) and repeat the evaluation proess beginning at above step 1. If the indoor fan set-up annot be further hanged, redue the air volume rate until the appliable Table 2 minimum is equaled. Use this redued air volume rate for all tests that require the Heating Full-load Air Volume Rate. b. For duted heating-only heat pumps that are tested with a variable-speed, onstant-air-volume-rate indoor fan installed. For all tests that speify the Heating Full-load Air Volume Rate, obtain an external stati pressure that does not ause instability or an automati shutdown of the indoor blower while being as lose to, but not less than, the appliable Table 2 minimum.. For duted heating-only heat pumps that are tested without an indoor fan installed. For the H1 or H1 2 Test, (exlusively), the pressure drop aross the indoor oil assembly must not exeed 0.30 inhes of water. If this pressure drop is exeeded, redue the air volume rate until the measured pressure drop equals the speified maximum. Use this redued air volume rate for all tests that require the Heating Full-load Air Volume Rate Non-duted heat pumps, inluding non-duted heating-only heat pumps. For non-duted heat pumps, the Heating Full-load Air Volume Rate is the air volume rate that results during eah test when the unit operates at an external stati pressure of zero inhes of water Heating Minimum Air Volume Rate. a. For duted heat pumps that regulate the speed (as opposed to the fm) of the indoor fan, Heating Minimum Fan Speed Heating Minimum Air Vol. Rate = Heating Full-load Air Vol. Rate, H1 Test Fan Speed 2 where Heating Minimum Fan Speed orresponds to the fan speed used when operating at low ompressor apaity (twoapaity system), the lowest fan speed used at any time when operating at the minimum ompressor speed (variable-speed system), or the lowest fan speed used when heating (single-speed ompressor and a variable-speed variable-air-volume-rate indoor fan). For suh heat pumps, obtain the Heating Minimum Air Volume Rate without regard to the external stati pressure. b. For duted heat pumps that regulate the air volume rate delivered by the indoor fan, the manufaturer must speify the Heating Minimum Air Volume Rate. For suh heat pumps, ondut all tests that speify the Heating Minimum Air Volume Rate (i.e., the H0 1, H1 1, H2 1, and H3 1 Tests) at an external stati pressure that does not ause instability or an automati shutdown of the indoor blower while being as lose to, but not less than, Htg Minimum Air Vol.Rate H01, H1 1, H21, H31, Test Pst = Pst,H1 2 Htg Full- load Air Vol.Rate 2, where ΔP st,h12 is the minimum external stati pressure that was targeted during the H1 2 Test.. For duted two-apaity northern heat pumps that are tested with an indoor fan installed, use the appropriate approah of the above two ases. 59

70 ANSI/ANSI/AHRI STANDARD 210/ d. For duted two-apaity heat pumps that are tested without an indoor fan installed, use the Cooling Minimum Air Volume Rate as the Heating Minimum Air Volume Rate. For duted two-apaity northern heat pumps that are tested without an indoor fan installed, use the Cooling Full-load Air Volume Rate as the Heating Minimum Air Volume Rate. For duted twoapaity heating-only heat pumps that are tested without an indoor fan installed, the Heating Minimum Air Volume Rate is the higher of the rate speified by the manufaturer or 75 perent of the Heating Full-load Air Volume Rate. During the laboratory tests on a oil-only (fanless) unit, obtain the Heating Minimum Air Volume Rate without regard to the pressure drop aross the indoor oil assembly. e. For non-duted heat pumps, the Heating Minimum Air Volume Rate is the air volume rate that results during eah test when the unit operates at an external stati pressure of zero inhes of water and at the indoor fan setting used at low ompressor apaity (two-apaity system) or minimum ompressor speed (variable-speed system). For units having a single-speed ompressor and a variable-speed, variable-air-volume-rate indoor fan, use the lowest fan setting allowed for heating Heating Intermediate Air Volume Rate. a. For duted heat pumps that regulate the speed of the indoor fan, H2 Test Fan Speed V Heating Intermediate Air Volume Rate = Heating Full-load Air Volume Rate, H1 Test Fan Speed 2 For suh heat pumps, obtain the Heating Intermediate Air Volume Rate without regard to the external stati pressure. b. For duted heat pumps that regulate the air volume rate delivered by the indoor fan, the manufaturer must speify the Heating Intermediate Air Volume Rate. For suh heat pumps, ondut the H2 V Test at an external stati pressure that does not ause instability or an automati shutdown of the indoor blower while being as lose to, but not less than, Heating Intermediate Air Volume Rate H2V Test Pst = Pst,H1 2 Heating Full- load Air Volume Rate 2, where ΔP st,h12 is the minimum external stati pressure that was speified for the H1 2 Test.. For non-duted heat pumps, the Heating Intermediate Air Volume Rate is the air volume rate that results when the heat pump operates at an external stati pressure of zero inhes of water and at the fan speed seleted by the ontrols of the unit for the H2 V Test onditions Heating Nominal Air Volume Rate. Exept for the noted hanges, determine the Heating Nominal Air Volume Rate using the approah desribed in setion Required hanges inlude substituting H1 N Test for H2 V Test within the first setion equation, substituting H1 N Test ΔP st for H2 V Test ΔP st in the seond setion equation, substituting H1 N Test for eah H2 V Test, and substituting Heating Nominal Air Volume Rate for eah Heating Intermediate Air Volume Rate. H1 Test Fan Speed N Heating Nominal Air Volume Rate = Heating Full-load Air Volume Rate, H1 Test Fan Speed 2 Heating Nominal Air Volume Rate H1N Test Pst = Pst,H1 2 Heating Full- load Air Volume Rate Indoor test room requirement when the air surrounding the indoor unit is not supplied from the same soure as the air entering the indoor unit. If using a test set-up where air is duted diretly from the air reonditioning apparatus to the indoor oil inlet (see Figure 2, Loop Air-Enthalpy Test Method Arrangement, of ASHRAE Standard ) (inorporated by referene, see ), maintain the dry bulb temperature within the test room within ±5.0 F of the appliable setions 3.2 and 3.6 dry bulb temperature test ondition for the air entering the indoor unit. 2, 60

71 ANSI/AHRI STANDARD 210/ Air volume rate alulations. For all steady-state tests and for frost aumulation (H2, H2 1, H2 2, H2 V ) tests, alulate the air volume rate through the indoor oil as speified in setions and of ASHRAE Standard (inorporated by referene, see ). (Note: In the first printing of ASHRAE Standard , the seond IP equation for Q mi should read, 1097 CA ν.) When using the Outdoor Air Enthalpy Method, follow setions and n P V n to alulate the air volume rate through the outdoor oil. To express air volume rates in terms of standard air, use: where, V s = air volume rate of standard (dry) air, (ft 3 /min) da V mx = air volume rate of the air-water vapor mixture, (ft 3 /min) mx v n ' = speifi volume of air-water vapor mixture at the nozzle, ft 3 per lbm of the air-water vapor mixture W n = humidity ratio at the nozzle, lbm of water vapor per lbm of dry air = the density assoiated with standard (dry) air, (lbm/ft 3 ) v n = speifi volume of the dry air portion of the mixture evaluated at the dry-bulb temperature, vapor ontent, and barometri pressure existing at the nozzle, ft 3 per lbm of dry air Test sequene. When testing a duted unit (exept if a heating-only heat pump), ondut the A or A 2 Test first to establish the Cooling Full-load Air Volume Rate. For duted heat pumps where the Heating and Cooling Full-load Air Volume Rates are different, make the first heating mode test one that requires the Heating Full-load Air Volume Rate. For duted heating-only heat pumps, ondut the H1 or H1 2 Test first to establish the Heating Full-load Air Volume Rate. When onduting an optional yli test, always ondut it immediately after the steady-state test that requires the same test onditions. For variable-speed systems, the first test using the Cooling Minimum Air Volume Rate should preede the E V Test if one expets to adjust the indoor fan ontrol options when preparing for the first Minimum Air Volume Rate test. Under the same irumstanes, the first test using the Heating Minimum Air Volume Rate should preede the H2 V Test. The test laboratory makes all other deisions on the test sequene Requirement for the air temperature distribution leaving the indoor oil. For at least the first ooling mode test and the first heating mode test, monitor the temperature distribution of the air leaving the indoor oil using the grid of individual sensors desribed in setions 2.5 and For the 30-minute data olletion interval used to determine apaity, the maximum spread among the outlet dry bulb temperatures from any data sampling must not exeed 1.5 F. Install the mixing devies desribed in setion to minimize the temperature spread Control of auxiliary resistive heating elements. Exept as noted, disable heat pump resistane elements used for heating indoor air at all times, inluding during defrost yles and if they are normally regulated by a heat omfort ontroller. For heat pumps equipped with a heat omfort ontroller, enable the heat pump resistane elements only during the belowdesribed, short test. For single-speed heat pumps overed under setion 3.6.1, the short test follows the H1 or, if onduted, the H1C Test. For two-apaity heat pumps and heat pumps overed under setion 3.6.2, the short test follows the H1 2 Test. Set the heat omfort ontroller to provide the maximum supply air temperature. With the heat pump operating and while maintaining the Heating Full-load Air Volume Rate, measure the temperature of the air leaving the indoor-side beginning 5 minutes after ativating the heat omfort ontroller. Sample the outlet dry-bulb temperature at regular intervals that span 5 minutes or less. Collet data for 10 minutes, obtaining at least 3 samples. Calulate the average outlet temperature over the 10-minute interval, T CC. 61

72 ANSI/ANSI/AHRI STANDARD 210/ Cooling mode tests for different types of air onditioners and heat pumps Tests for a unit having a single-speed ompressor that is tested with a fixed-speed indoor fan installed, with a onstantair-volume-rate indoor fan installed, or with no indoor fan installed. Condut two steady-state wet oil tests, the A and B Tests. Use the two optional dry-oil tests, the steady-state C Test and the yli D Test, to determine the ooling mode yli degradation oeffiient, C D. If the two optional tests are onduted but yield a tested C D that exeeds the default C D of if the two optional tests are not onduted, assign C D the default value of Table 3 speifies test onditions for these four tests Tests for a unit having a single-speed ompressor and a variable-speed variable-air-volume-rate indoor fan installed Indoor fan apaity modulation that orrelates with the outdoor dry bulb temperature. Condut four steady-state wet oil tests: The A 2, A 1, B 2, and B 1 Tests. Use the two optional dry-oil tests, the steady-state C 1 Test and the yli D 1 Test, to determine the ooling mode yli-degradation oeffiient, C D. If the two optional tests are onduted but yield a tested C D that exeeds the default C D or if the two optional tests are not onduted, assign C D the default value of Table 4 speifies test onditions for these six tests Indoor fan apaity modulation based on adjusting the sensible to total (S/T) ooling apaity ratio. The testing requirements are the same as speified in setion and Table 3. Use a Cooling Full-load Air Volume Rate that represents a normal residential installation. If performed, ondut the steady-state C Test and the yli D Test with the unit operating in the same S/T apaity ontrol mode as used for the B Test. 62

73 ANSI/AHRI STANDARD 210/ Table 3. Cooling Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed-Speed Indoor Fan, a Constant Air Volume Rate Indoor Fan, or No Indoor Fan Test desription Air Entering Indoor Unit Temperature ( F) Air Entering Outdoor Unit Temperature ( F) Dry Bulb Wet Bulb Dry Bulb Wet Bulb Cooling Air Volume Rate A Test required (steady, wet oil) Cooling Full-load 2 B Test required (steady, wet oil) Cooling Full-load 2 C Test optional (steady, dry oil) (3) Cooling Full-load 2 D Test optional (yli, dry oil) (3) (4) Notes: (1) The speified test ondition only applies if the unit rejets ondensate to the outdoor oil. (2) Defined in setion (3) The entering air must have a low enough moisture ontent so no ondensate forms on the indoor oil. (It is reommended that an indoor wet-bulb temperature of 57 F or less be used.) (4) Maintain the airflow nozzles stati pressure differene or veloity pressure during the ON period at the same pressure differene or veloity pressure as measured during the C 1 Test. 63

74 ANSI/ANSI/AHRI STANDARD 210/ Table 4. Cooling Mode Test Conditions for Units Having a Single-Speed Compressor and a Variable Air Volume Rate Indoor Fan That orrelates With the Outdoor Dry Bulb Temperature (Se ) Test desription A 2 Test required (steady, wet oil)... Air Entering Indoor Unit Temperature ( F) Dry Bulb 80 Wet Bulb 67 Air Entering Outdoor Unit Temperature ( F) Dry Bulb 95 Wet Bulb 75 (1) Cooling Air Volume Rate Cooling Full-load (2) A 1 Test required (steady, wet oil) (1) Cooling minimum (3) B 2 Test required (steady, wet oil) (1) Cooling Full-load (2) B 1 Test required (steady, wet oil) (1) Cooling minimum (3) C 1 Test (4) optional (steady, dry oil) (4) Cooling minimum (3) D 1 Test (4) optional (yli, dry oil) (4) (5) Notes: (1) The speified test ondition only applies if the unit rejets ondensate to the outdoor oil. (2) Defined in setion (3) Defined in setion (4) The entering air must have a low enough moisture ontent so no ondensate forms on the indoor oil. (It is reommended that an indoor wet-bulb temperature of 57 F or less be used.) (5) Maintain the airflow nozzles stati pressure differene or veloity pressure during the ON period at the same pressure differene or veloity pressure as measured during the C 1 Test Tests for a unit having a two-apaity ompressor. (See Definition 1.45.) a. Condut four steady-state wet oil tests: the A 2, B 2, B 1, and F 1 Tests. Use the two optional dry-oil tests, the steady-state C 1 Test and the yli D 1 Test, to determine the ooling-mode yli-degradation oeffiient, C. If the two optional tests are onduted but yield a tested C that exeeds the default test onditions for these six tests. C D or if the two optional tests are not onduted, assign D C D the default value of Table 5 speifies b. For units having a variable speed indoor fan that is modulated to adjust the sensible to total (S/T) ooling apaity ratio, use Cooling Full-load and Cooling Minimum Air Volume Rates that represent a normal residential installation. Additionally, if onduting the optional dry-oil tests, operate the unit in the same S/T apaity ontrol mode as used for the B 1 Test.. Test two-apaity, northern heat pumps (see Definition 1.46) in the same way as a single speed heat pump with the unit operating exlusively at low ompressor apaity (see setion and Table 3). d. If a two-apaity air onditioner or heat pump loks out low-apaity operation at higher outdoor temperatures, then use the two optional dry-oil tests, the steady-state C 2 Test and the yli D 2 Test, to determine the ooling-mode ylidegradation oeffiient that only applies to on/off yling from high apaity, C D ( k = 2). If the two optional tests are onduted but yield a tested C D ( k = 2) that exeeds the default C D ( k = 2) or if the two optional tests are not onduted, assign C D ( k = 2) the default value. The default C D ( k = 2) is the same value as determined or assigned for the lowapaity yli-degradation oeffiient, C [or equivalently, C D ( k = 1) ]. D D 64

75 Test Desription Table 5. Cooling Mode Test Conditions for Units Having a Two-Capaity Compressor Air Entering Air Entering Indoor Unit Outdoor Unit Temperature ( F) Dry Wet Bulb Bulb Temperature ( F) Dry Wet Bulb Bulb ANSI/AHRI STANDARD 210/ Compressor Capaity A 2 Test required (1) High (steady, wet oil) B 2 Test required (1) High (steady, wet oil) B 1 Test required (1) Low (steady, wet oil) C 2 Test optional (4) High (steady, dry-oil) D 2 Test optional (4) (5) High (yli, dry-oil) C 1 Test optional (4) Low (steady, dry-oil) D 1 Test optional (4) (6) Low (yli, dry-oil) F 1 Test required (1) Low (steady, wet oil) (1) The speified test ondition only applies if the unit rejets ondensate to the outdoor oil. Cooling Air Volume Rate Cooling Full- Load 2) Cooling Full- Load 2) Cooling Minimum (3) Cooling Full- Load (2) Cooling Minimum (3) Cooling Minimum (3) (2) Defined in setion (3) Defined in setion (4) The entering air must have a low enough moisture ontent so no ondensate forms on the indoor oil. DOE reommends using an indoor air wet-bulb temperature of 57 F or less. (5) Maintain the airflow nozzle(s) stati pressure differene or veloity pressure during the ON period at the same pressure or veloity as measured during the C 2 Test. (6) Maintain the airflow nozzle(s) stati pressure differene or veloity pressure during the ON period at the same pressure or veloity as measured during the C 1 Test Tests for a unit having a variable-speed ompressor. a. Condut five steady-state wet oil tests: The A 2, E V, B 2, B 1, and F 1 tests. Use the two optional dry-oil tests, the steady-state G 1 Test and the yli I 1 Test, to determine the ooling mode yli-degradation oeffiient, C D. If the two optional tests are onduted but yield a tested C D that exeeds the default C D or if the two optional tests are not onduted, assign C D the default value of Table 6 speifies test onditions for these seven tests. Determine the intermediate ompressor speed ited in Table 6 using: 65

76 ANSI/ANSI/AHRI STANDARD 210/ where a tolerane of plus 5 perent or the next higher inverter frequeny step from that alulated is allowed. b. For units that modulate the indoor fan speed to adjust the sensible to total (S/T) ooling apaity ratio, use Cooling Fullload, Cooling Intermediate, and Cooling Minimum Air Volume Rates that represent a normal residential installation. Additionally, if onduting the optional dry-oil tests, operate the unit in the same S/T apaity ontrol mode as used for the F 1 Test.. For multiple-split air onditioners and heat pumps (exept where noted), the following proedures supersede the above requirements: For all Table 6 tests speified for a minimum ompressor speed, at least one indoor unit must be turned off. The manufaturer shall designate the partiular indoor unit(s) that is turned off. The manufaturer must also speify the ompressor speed used for the Table 6 E V Test, a ooling-mode intermediate ompressor speed that falls within ¼ and ¾ of the differene between the maximum and minimum ooling-mode speeds. The manufaturer should presribe an intermediate speed that is expeted to yield the highest EER for the given E V Test onditions and braketed ompressor speed range. The manufaturer an designate that one or more indoor units are turned off for the E V Test. 66

77 Test Desription A 2 Test required (steady, wet oil) B 2 Test required (steady wet oil) E V Test required (steady, wet oil) B 1 Test required (steady, wet oil) F 1 Test required (steady, wet oil) G 1 Test (5) optional (steady, dryoil) I 1 Test (5) optional Table 6. Cooling Mode Test Condition for Units Having a Variable-Speed Compressor Air Entering Air Entering Indoor Unit Temperature ( F) Dry Bulb Wet Bulb Outdoor Unit Temperature ( F) Dry Bulb Wet Bulb ANSI/AHRI STANDARD 210/ Compressor Speed (1) Maximum (1) Maximum (1) Intermediate (1) Minimum (1) Minimum (6) (6) 67 Minimum 67 Minimum Cooling Air Volume Rate Cooling Full- Load (2) Cooling Full- Load (2) Cooling Intermediate (3) Cooling Minimum (4) Cooling Minimum (4) Cooling Minimum (4) (yli, dry-oil) (1) The speified test ondition only applies if the unit rejets ondensate to the outdoor oil. (6) (2) Defined in setion (3) Defined in setion (4) Defined in setion (5) The entering air must have a low enough moisture ontent so no ondensate forms on the indoor oil. DOE reommends using an indoor air wet bulb temperature of 57 F or less. (6) Maintain the airflow nozzle(s) stati pressure differene or veloity pressure during the ON period at the same pressure differene or veloity pressure as measured during the G 1 Test. 67

78 ANSI/ANSI/AHRI STANDARD 210/ Test proedures for steady-state wet oil ooling mode tests (the A, A 2, A 1, B, B 2, B 1, E V, and F 1 Tests). a. For the pretest interval, operate the test room reonditioning apparatus and the unit to be tested until maintaining equilibrium onditions for at least 30 minutes at the speified setion 3.2 test onditions. Use the exhaust fan of the airflow measuring apparatus and, if installed, the indoor fan of the test unit to obtain and then maintain the indoor air volume rate and/or external stati pressure speified for the partiular test. Continuously reord (see Definition 1.15): (1) The dry-bulb temperature of the air entering the indoor oil, (2) The water vapor ontent of the air entering the indoor oil, (3) The dry-bulb temperature of the air entering the outdoor oil, and (4) For the setion ases where its ontrol is required, the water vapor ontent of the air entering the outdoor oil. Refer to setion 3.11 for additional requirements that depend on the seleted seondary test method. b. After satisfying the pretest equilibrium requirements, make the measurements speified in Table 3 of ASHRAE Standard (inorporated by referene, see ) for the Indoor Air Enthalpy method and the user-seleted seondary method. Exept for external stati pressure, make the Table 3 measurements at equal intervals that span 10 minutes or less. Measure external stati pressure every 5 minutes or less. Continue data sampling until reahing a 30-minute period (e.g., four onseutive 10-minute samples) where the test toleranes speified in Table 7 are satisfied. For those ontinuously reorded parameters, use the entire data set from the 30-minute interval to evaluate Table 7 ompliane. Determine the average eletrial power onsumption of the air onditioner or heat pump over the same 30-minute interval.. Calulate indoor-side total ooling apaity as speified in setions and of ASHRAE Standard (inorporated by referene, see ). Do not adjust the parameters used in alulating apaity for the permitted variations in test onditions. Evaluate air enthalpies based on the measured barometri pressure. Assign the average total spae ooling apaity and eletrial power onsumption over the 30-minute data olletion interval to the variables Q k (T) and E k (T), respetively. For these two variables, replae the T with the nominal outdoor temperature at whih the test was onduted. The supersript k is used only when testing multi-apaity units. Use the supersript k=2 to denote a test with the unit operating at high apaity or maximum speed, k=1 to denote low apaity or minimum speed, and k=v to denote the intermediate speed. d. For units tested without an indoor fan installed, derease Q k (T) by and inrease E k (T) by, where V s is the average measured indoor air volume rate expressed in units of ubi feet per minute of standard air (sfm). 68

79 ANSI/AHRI STANDARD 210/ Table 7. Test Operating and Test Condition Toleranes for Setion 3.3 Steady-State Wet Coil Cooling Mode Tests and Setion 3.4 Dry Coil Cooling Mode Tests Indoor dry-bulb, F Test Operating Tolerane (1) Test Condition Tolerane (2) Entering temperature... Leaving temperature... Indoor wet-bulb, F Entering temperature... Leaving temperature... Outdoor dry-bulb, F Entering temperature... Leaving temperature... Outdoor wet-bulb, F Entering temperature... Leaving temperature... External resistane to airflow, inhes of water... Eletrial voltage, % of rdg.... Nozzle pressure drop, % of rdg.... Notes: (1) See Definition (3) (4) (4) (3) (5) 0.02 (6) 1.5 (2) See Definition (3) Only applies during wet oil tests; does not apply during steady-state, dry oil ooling mode tests. (4) Only applies when using the Outdoor Air Enthalpy Method. (5) Only applies during wet oil ooling mode tests where the unit rejets ondensate to the outdoor oil. (6) Only applies when testing non-duted units. d. For air onditioners and heat pumps having a onstant-air-volume-rate indoor fan, the five additional steps listed below are required if the average of the measured external stati pressures exeeds the appliable setions minimum (or target) external stati pressure (ΔP min ) by 0.03 inhes of water or more. 1. Measure the average power onsumption of the indoor fan motor ( E fan,1) and reord the orresponding external stati pressure (ΔP 1 ) during or immediately following the 30-minute interval used for determining apaity. 2. After ompleting the 30-minute interval and while maintaining the same test onditions, adjust the exhaust fan of the airflow measuring apparatus until the external stati pressure inreases to approximately ΔP 1 + (ΔP 1 ΔP min ). 69

80 ANSI/ANSI/AHRI STANDARD 210/ After re-establishing steady readings of the fan motor power and external stati pressure, determine average values for the indoor fan power ( E fan,2) and the external stati pressure (ΔP 2 ) by making measurements over a 5-minute interval. 4. Approximate the average power onsumption of the indoor fan motor at ΔP min using linear extrapolation: 5. Inrease the total spae ooling apaity, Q k (T), by the quantity ( E fan, 1 E fan, min), when expressed on a Btu/h basis. Derease the total eletrial power, E k (T), by the same fan power differene, now expressed in watts. 3.4 Test proedures for the optional steady-state dry-oil ooling-mode tests (the C, C 1, C 2, and G 1 Tests). a. Exept for the modifiations noted in this setion, ondut the steady-state dry oil ooling mode tests as speified in setion 3.3 for wet oil tests. Prior to reording data during the steady-state dry oil test, operate the unit at least one hour after ahieving dry oil onditions. Drain the drain pan and plug the drain opening. Thereafter, the drain pan should remain ompletely dry. b. Denote the resulting total spae ooling apaity and eletrial power derived from the test as Q ss, dry and E ss, dry. With regard to a setion 3.3 deviation, do not adjust Q ss, dry for dut losses (i.e., do not apply setion of ASHRAE Standard (inorporated by referene, see )). In preparing for the setion 3.5 yli tests, reord the average indoorside air volume rate, V, speifi heat of the air, Cp,a (expressed on dry air basis), speifi volume of the air at the nozzles, v n, humidity ratio at the nozzles, W n, and either pressure differene or veloity pressure for the flow nozzles. For units having a variable-speed indoor fan (that provides either a onstant or variable air volume rate) that will or may be tested during the yli dry oil ooling mode test with the indoor fan turned off (see setion 3.5), inlude the eletrial power used by the indoor fan motor among the reorded parameters from the 30-minute test. 3.5 Test proedures for the optional yli dry-oil ooling-mode tests (the D, D 1, D 2, and I 1 Tests). a. After ompleting the steady-state dry-oil test, remove the Outdoor Air Enthalpy method test apparatus, if onneted, and begin manual OFF/ON yling of the unit's ompressor. The test set-up should otherwise be idential to the set-up used during the steadystate dry oil test. When testing heat pumps, leave the reversing valve during the ompressor OFF yles in the same position as used for the ompressor ON yles, unless automatially hanged by the ontrols of the unit. For units having a variablespeed indoor fan, the manufaturer has the option of eleting at the outset whether to ondut the yli test with the indoor fan enabled or disabled. Always revert to testing with the indoor fan disabled if yli testing with the fan enabled is unsuessful. b. For units having a single-speed or two-apaity ompressor, yle the ompressor OFF for 24 minutes and then ON for 6 minutes (Δτ y,dry = 0.5 hours). For units having a variable-speed ompressor, yle the ompressor OFF for 48 minutes and then ON for 12 minutes (Δτ y, dry = 1.0 hours). Repeat the OFF/ON ompressor yling pattern until the test is ompleted. Allow the ontrols of the unit to regulate yling of the outdoor fan.. Setions and speify airflow requirements through the indoor oil of duted and non-duted systems, respetively. In all ases, use the exhaust fan of the airflow measuring apparatus (overed under setion 2.6) along with the indoor fan of the unit, if installed and operating, to approximate a step response in the indoor oil airflow. Regulate the exhaust fan to quikly obtain and then maintain the flow nozzle stati pressure differene or veloity pressure at the same value as was measured during the steady-state dry oil test. The pressure differene or veloity pressure should be within 2 perent of the value from the steady-state dry oil test within 15 seonds after airflow initiation. For units having a variablespeed indoor fan that ramps when yling on and/or off, use the exhaust fan of the airflow measuring apparatus to impose a step response that begins at the initiation of ramp up and ends at the termination of ramp down. d. For units having a variable-speed indoor fan, ondut the yli dry oil test using the pull-thru approah desribed below if any of the following our when testing with the fan operating: (1) The test unit automatially yles off; (2) Its blower motor reverses; or 70

81 ANSI/AHRI STANDARD 210/ (3) The unit operates for more than 30 seonds at an external stati pressure that is 0.1 inhes of water or more higher than the value measured during the prior steady-state test. For the pull-thru approah, disable the indoor fan and use the exhaust fan of the airflow measuring apparatus to generate the speified flow nozzles stati pressure differene or veloity pressure. If the exhaust fan annot deliver the required pressure differene beause of resistane reated by the unpowered blower, temporarily remove the blower. e. After ompleting a minimum of two omplete ompressor OFF/ON yles, determine the overall ooling delivered and total eletrial energy onsumption during any subsequent data olletion interval where the test toleranes given in Table 8 are satisfied. If available, use eletri resistane heaters (see setion 2.1) to minimize the variation in the inlet air temperature. f. With regard to the Table 8 parameters, ontinuously reord the dry-bulb temperature of the air entering the indoor and outdoor oils during periods when air flows through the respetive oils. Sample the water vapor ontent of the indoor oil inlet air at least every 2 minutes during periods when air flows through the oil. Reord external stati pressure and the air volume rate indiator (either nozzle pressure differene or veloity pressure) at least every minute during the interval that air flows through the indoor oil. (These regular measurements of the airflow rate indiator are in addition to the required measurement at 15 seonds after flow initiation.) Sample the eletrial voltage at least every 2 minutes beginning 30 seonds after ompressor start-up. Continue until the ompressor, the outdoor fan, and the indoor fan (if it is installed and operating) yle off. g. For duted units, ontinuously reord the dry-bulb temperature of the air entering (as noted above) and leaving the indoor oil. Or if using a thermopile, ontinuously reord the differene between these two temperatures during the interval that air flows through the indoor oil. For non-duted units, make the same dry-bulb temperature measurements beginning when the ompressor yles on and ending when indoor oil airflow eases. h. Integrate the eletrial power over omplete yles of length Δτ y, dry. For duted units tested with an indoor fan installed and operating, integrate eletrial power from indoor fan OFF to indoor fan OFF. For all other duted units and for nonduted units, integrate eletrial power from ompressor OFF to ompressor OFF. (Some yli tests will use the same data olletion intervals to determine the eletrial energy and the total spae ooling. For other units, terminate data olletion used to determine the eletrial energy before terminating data olletion used to determine total spae ooling.) Table 8. Test Operating and Test Condition Toleranes for Cyli Dry Coil Cooling Mode Tests Indoor entering dry-bulb temperature (3), F... Test Operating Tolerane (1) Test Condition Tolerane (2) Indoor entering wet-bulb temperature, F... Outdoor entering dry-bulb temperature (3), F... External resistane to airflow (3), inhes of water... Airflow nozzle pressure differene or veloity pressure (3), % of reading (4) (5) Eletrial voltage (6), % of rdg.... Notes: (1) See Definition (2) See Definition (3) Applies during the interval that air flows through the indoor (outdoor) oil exept for the first 30 seonds after flow initiation. For units having a variable-speed indoor fan that ramps, the toleranes listed for the external resistane to airflow apply from 30 seonds after ahieving full speed until ramp down begins. (4) Shall at no time exeed a wet-bulb temperature that results in ondensate forming on the indoor oil. (5) The test ondition shall be the average nozzle pressure differene or veloity pressure measured during the steadystate dry oil test. (6) Applies during the interval when at least one of the following the ompressor, the outdoor fan, or, if appliable, the indoor fan are operating exept for the first 30 seonds after ompressor start-up

82 ANSI/ANSI/AHRI STANDARD 210/ i. If the Table 8 toleranes are satisfied over the omplete yle, reord the measured eletrial energy onsumption as e y, dry and express it in units of watt-hours. Calulate the total spae ooling delivered, q y,dry, in units of Btu using, where V, C p,a, v n ' (or v n ), and W n are the values reorded during the setion 3.4 dry oil steady-state test and, T al (τ) = dry bulb temperature of the air entering the indoor oil at time τ, F. T a2 (τ) = dry bulb temperature of the air leaving the indoor oil at time τ, F. τ 1 = for duted units, the elapsed time when airflow is initiated through the indoor oil; for non-duted units, the elapsed time when the ompressor is yled on, hr. τ 2 = the elapsed time when indoor oil airflow eases, hr Proedures when testing duted systems. The automati ontrols that are normally installed with the test unit must govern the OFF/ON yling of the air moving equipment on the indoor side (exhaust fan of the airflow measuring apparatus and, if installed, the indoor fan of the test unit). For example, for duted units tested without an indoor fan installed but rated based on using a fan time delay relay, ontrol the indoor oil airflow aording to the rated ON and/or OFF delays provided by the relay. For duted units having a variable-speed indoor fan that has been disabled (and possibly removed), start and stop the indoor airflow at the same instanes as if the fan were enabled. For all other duted units tested without an indoor fan installed, yle the indoor oil airflow in unison with the yling of the ompressor. Close air dampers on the inlet (setion 2.5.1) and outlet side (setions 2.5 and 2.5.4) during the OFF period. Airflow through the indoor oil should stop within 3 seonds after the automati ontrols of the test unit (at to) de-energize the indoor fan. For duted units tested without an indoor fan installed (exluding the speial ase where a variable-speed fan is temporarily removed), inrease e y,dry by the quantity, and derease q y,dry by, Where V s is the average indoor air volume rate from the setion 3.4 dry oil steady-state test and is expressed in units of ubi feet per minute of standard air (sfm). For units having a variable-speed indoor fan that is disabled during the yli test, inrease e y,dry and derease q y,dry based on: a. The produt of [τ 2 τ1 ] and the indoor fan power measured during or following the dry oil steady-state test; or, b. The following algorithm if the indoor fan ramps its speed when yling. 1. Measure the eletrial power onsumed by the variable-speed indoor fan at a minimum of three operating onditions: at the speed/air volume rate/external stati pressure that was measured during the steady-state test, at 72

83 ANSI/AHRI STANDARD 210/ operating onditions assoiated with the midpoint of the ramp-up interval, and at onditions assoiated with the midpoint of the ramp-down interval. For these measurements, the toleranes on the airflow volume or the external stati pressure are the same as required for the setion 3.4 steady-state test. 2. For eah ase, determine the fan power from measurements made over a minimum of 5 minutes. 3. Approximate the eletrial energy onsumption of the indoor fan if it had operated during the yli test using all three power measurements. Assume a linear profile during the ramp intervals. The manufaturer must provide the durations of the ramp-up and ramp-down intervals. If a manufaturer-supplied ramp interval exeeds 45 seonds, use a 45-seond ramp interval nonetheless when estimating the fan energy. The manufaturer is allowed to hoose option a, and forego the extra testing burden of option b, even if the unit ramps indoor fan speed when yling Proedures when testing non-duted systems. Do not use air dampers when onduting yli tests on non-duted units. Until the last OFF/ON ompressor yle, airflow through the indoor oil must yle off and on in unison with the ompressor. For the last OFF/ON ompressor yle the one used to determine e y,dry and q y,dry use the exhaust fan of the airflow measuring apparatus and the indoor fan of the test unit to have indoor airflow start 3 minutes prior to ompressor uton and end three minutes after ompressor utoff. Subtrat the eletrial energy used by the indoor fan during the 3 minutes prior to ompressor ut-on from the integrated eletrial energy, e y, dry. Add the eletrial energy used by the indoor fan during the 3 minutes after ompressor utoff to the integrated ooling apaity, q y, dry. For the ase where the non-duted unit uses a variable-speed indoor fan whih is disabled during the yli test, orret e y,dry and q y,dry using the same approah as presribed in setion for duted units having a disabled variable-speed indoor fan Cooling-mode yli-degradation oeffiient alulation. Use the two optional dry-oil tests to determine the ooling-mode yli-degradation oeffiient, C D. Append (k=2) to the oeffiient if it orresponds to a two-apaity unit yling at high apaity. If the two optional tests are onduted but yield a tested C D that exeeds the default C D or if the two optional tests are not onduted, assign CD the default value of The default value for two-apaity units yling at high apaity, however, is the low-apaity oeffiient, i.e., C D ( k = 2) = C D. Evaluate CD using the above results and those from the setion 3.4 dry-oil steady-state test. where, the average energy effiieny ratio during the yli dry oil ooling mode test, Btu/W h the average energy effiieny ratio during the steady-state dry oil ooling mode test, Btu/W h the ooling load fator dimensionless. 73

84 ANSI/ANSI/AHRI STANDARD 210/ Round the alulated value for C D to the nearest If C D is negative, then set it equal to zero. 3.6 Heating mode tests for different types of heat pumps, inluding heating-only heat pumps Tests for a heat pump having a single-speed ompressor that is tested with a fixed speed indoor fan installed, with a onstant-air-volume-rate indoor fan installed, or with no indoor fan installed. Condut the optional High Temperature Cyli h (H1C) Test to determine the heating mode yli-degradation oeffiient, C D. If this optional test is onduted but yields a h h h tested C D that exeeds the default C D or if the optional test is not onduted, assign C D the default value of Test onditions for the four tests are speified in Table Tests for a heat pump having a single-speed ompressor and a variable-speed, variable-air-volume-rate indoor fan: apaity modulation orrelates with outdoor dry bulb temperature. Condut five tests: two High Temperature Tests (H1 2 and H1 1 ), one Frost Aumulation Test (H2 2 ), and two Low Temperature Tests (H3 2 and H3 1 ). Conduting an additional Frost Aumulation Test (H2 1 ) is optional. Condut the optional High Temperature Cyli (H1C 1 ) Test to determine the heating h h mode yli-degradation oeffiient, C D. If this optional test is onduted but yields a tested C D that exeeds the default h h C D or if the optional test is not onduted, assign C D the default value of Test onditions for the seven tests are speified in Table 10. If the optional H2 1 Test is not performed, use the following equations to approximate the apaity and eletrial power of the heat pump at the H2 1 test onditions: Table 9. Heating Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed-Speed Indoor Fan, a Constant Air Volume Rate Indoor Fan, or No Indoor Fan Test desription H1 Test (required, steady)... Air Entering Indoor Unit Temperature ( F) Dry Bulb 70 Wet Bulb 60 (max) Air Entering Outdoor Unit Temperature ( F) Dry Bulb 47 Wet Bulb 43 Heating Air Volume Rate Heating Full-load (1) H1C Test (optional, yli) (max) (2) H2 Test (required) (max) Heating Full-load (1) H3 Test (required, steady) (max) Heating Full-load (1) Notes: (1) Defined in setion (2) Maintain the airflow nozzles stati pressure differene or veloity pressure during the ON period at the same pressure differene or veloity pressure as measured during the H1 Test. 74

85 ANSI/AHRI STANDARD 210/ Table 10. Heating Mode Test Conditions for Units Having a Single-Speed Compressor and a Variable Air Volume Rate Indoor Fan Test desription Air Entering Indoor Unit Temperature ( F) Air Entering Outdoor Unit Temperature ( F) Dry Bulb Wet Bulb Dry Bulb Wet Bulb Heating Air Volume Rate H1 2 Test (required, steady) (max) Heating Full-load (1) H1 1 Test (required, steady) (max) Heating Minimum (2) H1C 1 Test (optional, yli) (max) (3) H2 2 Test (required) (max) Heating Full-load (1) H2 1 Test (optional) (max) Heating Minimum (2) H3 2 Test (required, steady) (max) Heating Full-load (1) H3 1 Test (required, steady) (max) Heating Minimum (2) Notes: (1) Defined in setion (2) Defined in setion (3) Maintain the airflow nozzles stati pressure differene or veloity pressure during the ON period at the same pressure differene or veloity pressure as measured during the H1 1 Test. where, The quantities Q h k=2 (47), E h k=2 (47), Q h k=1 (47), and E h k=1 (47) are determined from the H1 2 and H1 1 Tests and evaluated as speified in setion 3.7; the quantities Q h k=2 (35) and E h k=2 (35) are determined from the H2 2 Test and evaluated as speified in setion 3.9; and the quantities Q h k=2 (17), E h k=2 (17), Q h k=1 (17), and E h k=1 (17), are determined from the H3 2 and H3 1 Tests and evaluated as speified in setion Tests for a heat pump having a two-apaity ompressor (see Definition 1.45), inluding two-apaity, northern heat pumps (see Definition 1.46). a. Condut one Maximum Temperature Test (H0 1 ), two High Temperature Tests (H1 2 and H1 1 ), one Frost Aumulation Test (H2 2 ), and one Low Temperature Test (H3 2 ). Condut an additional Frost Aumulation Test (H2 1 ) and Low Temperature Test (H3 1 ) if both of the following onditions exist: 1. Knowledge of the heat pump's apaity and eletrial power at low ompressor apaity for outdoor temperatures of 37 F and less is needed to omplete the setion seasonal performane alulations, and 2. The heat pump's ontrols allow low apaity operation at outdoor temperatures of 37 F and less. 75

86 ANSI/ANSI/AHRI STANDARD 210/ b. Condut the optional Maximum Temperature Cyli Test (H0C 1 ) to determine the heating mode yli degradation oeffiient, C D h. If this optional test is not onduted, assign C D h the default value of Table 10 speifies test onditions for these eight tests. 76

87 Table 11. Heating Mode Test Conditions for Units Having a Two-Capaity Compressor Air Entering Indoor Unit Air Entering Outdoor Unit Compressor Test Desription Temperature ( F) Temperature ( F) Capaity Dry Dry Wet Bulb Wet Bulb Bulb Bulb H0 1 Test (max) Low (required, steady) H1 2 Test (max) High (required, steady) H1C 2 Test (max) High (optional, yli) H1 1 Test (max) Low (required) H1C 1 Test (max) Low (optional, yli) H2 2 Test (max) High (required) H2 1 Test (5,6) (max) Low (required) H3 2 Test (max) High (required, steady) H3 1 Test (5) (max) Low (required, steady) (1) Defined in setion ANSI/AHRI STANDARD 210/ Heating Air Volume Rate Heating Minimum (1) Heating Full-Load (2) (3) Heating Minimum (1) (4) Heating Load (2) Heating Minimum (1) Heating Load (2) Heating Minimum (1) Full- Full- (2) Defined in setion (3) Maintain the airflow nozzle(s) stati pressure differene or veloity pressure during the ON period at the same pressure or veloity as measured during the H1 2 Test. (4) Maintain the airflow nozzle(s) stati pressure differene or veloity pressure during the ON period at the same pressure or veloity as measured during the H1 1 Test. (5) Required only if the heat pump s performane when operating at low ompressor apaity and outdoor temperatures less than 37 F is needed to omplete the setion HSPF alulations. (6) If table note #5 applies, the setion equations for Q k = 1 h (35) and E k = 1 h (17) may be used in lieu of onduting the H2 1 Test. 77

88 ANSI/ANSI/AHRI STANDARD 210/ Tests for a heat pump having a two-apaity ompressor (see Definition 1.45), inluding two-apaity, northern heat pumps (see Definition 1.46). a. Condut one Maximum Temperature Test (H0 1 ), two High Temperature Tests (H1 2 and H1 1 ), one Frost Aumulation Test (H2 2 ), and one Low Temperature Test (H3 2 ). Condut an additional Frost Aumulation Test (H2 1 ) and Low Temperature Test (H3 1 ) if both of the following onditions exist: 1. Knowledge of the heat pump s apaity and eletrial power at low ompressor apaity for outdoor temperatures of 37 F and less is needed to omplete the setion seasonal performane alulations; and 2. The heat pump s ontrols allow low-apaity operation at outdoor temperatures of 37 F and less. If the above two onditions are met, an alternative to onduting the H2 1 Frost Aumulation is to use the following equations to approximate the apaity and eletrial power: Q E k= 1 h k= 1 h { Q k= 1 k= 1 k= 1 h ( 17) [ Q h ( 47) Qh ( )]} k= 1 k= 1 k= 1 { E ( 17) [ E ( 47) E ( )]} ( 35) = ( 35) = h h Determine the quantities Q k= 1 (47) h and E k = 1 h (47) from the H1 1 Test and evaluate them aording to Setion 3.7. Determine the quantities Q k= 1 (17) h and E k= 1 (17) h from the H3 1 Test and evaluate them aording to Setion b. Condut the optional High Temperature Cyli Test (H1C 1 ) to determine the heating-mode yli-degradation oeffiient, h h h C D. If this optional test is onduted but yields a tested C D that exeeds the default C D or if the optional test is not h onduted, assign C D the default value of If a two-apaity heat pump loks out low apaity operation at lower outdoor temperatures, ondut the optional High Temperature Cyli Test (H1C 2 ) to determine the high-apaity heatingmode yli-degradation oeffiient, C h D ( k = 2). If this optional test at high apaity is onduted but yields a tested C h D ( k = 2) that exeeds the default C h D ( k = 2) or if the optional test is not onduted, assign C h D ( k = 2) the default value. The default C h D ( k = 2) is the same value as determined or assigned for the low-apaity yli-degradation oeffiient, C [or equivalently, C h D ( k = 1) ]. Table 11 speifies test onditions for these nine tests. h D Tests for a heat pump having a variable-speed ompressor. a. Condut one Maximum Temperature Test (H0 1 ), two High Temperature Tests (H1 2 and H1 1 ), one Frost Aumulation Test (H2 V ), and one Low Temperature Test (H3 2 ). Conduting one or both of the following tests is optional: An additional High Temperature Test (H1 N ) and an additional Frost Aumulation Test (H2 2 ). Condut the optional Maximum Temperature Cyli (H0C 1 ) Test to determine the heating h h mode yli-degradation oeffiient, C D. If this optional test is onduted but yields a tested C D that exeeds the default h h C D or if the optional test is not onduted, assign C D the default value of Test onditions for the eight tests are speified in Table 12. Determine the intermediate ompressor speed ited in Table 12 using the heating mode maximum and minimum ompressors speeds and: h where a tolerane of plus 5 perent or the next higher inverter frequeny step from that alulated is allowed. If the H2 2 Test is not done, use the following equations to approximate the apaity and eletrial power at the H2 2 test onditions: 78

89 ANSI/AHRI STANDARD 210/ b. Determine the quantities Q h k=2 (47) and from E h k=2 (47) from the H1 2 Test and evaluate them aording to setion 3.7. Determine the quantities Q h k=2 (17) and E h k=2 (17) from the H3 2 Test and evaluate them aording to setion For heat pumps where the heating mode maximum ompressor speed exeeds its ooling mode maximum ompressor speed, ondut the H1 N Test if the manufaturer requests it. If the H1 N Test is done, operate the heat pump's ompressor at the same speed as the speed used for the ooling mode A 2 Test. Refer to the last sentene of setion 4.2 to see how the results of the H1 N Test may be used in alulating the heating seasonal performane fator.. For multiple-split heat pumps (only), the following proedures supersede the above requirements. For all Table 12 tests speified for a minimum ompressor speed, at least one indoor unit must be turned off. The manufaturer shall designate the partiular indoor unit(s) that is turned off. The manufaturer must also speify the ompressor speed used for the Table 12 H2 V Test, a heating-mode intermediate ompressor speed that falls within ¼ and ¾ of the differene between the maximum and minimum heating-mode speeds. The manufaturer should presribe an intermediate speed that is expeted to yield the highest COP for the given H2 V Test onditions and braketed ompressor speed range. The manufaturer an designate that one or more speifi indoor units are turned off for the H2 V Test. Test Desription Table 12. Heating Mode Test Conditions for Units Having a Variable-Speed Compressor Air Entering Air Entering Indoor Unit Temperature ( F) Outdoor Unit Temperature ( F) Dry Bulb Wet Bulb Dry Bulb Wet Bulb Compressor Speed Heating Air Volume Rate H0 1 Test (max) Heating Minimum Minimum (1) (required, steady) H0C 1 Test (max) (2) Minimum (optional, steady) H1 2 Test (max) Heating Full Maximum Load (3) (required, steady) H1 1 Test (max) Heating Minimum Minimum (1) (required, steady) H1 N Test (max) Cooling Mode Heating Maximum Nominal (4) (optional, steady) H2 2 Test (max) Heating Full Maximum Load (3) (optional) H2 V Test (max) Heating Intermediate Intermediate (5) (required) H3 2 Test (max) Heating Full Maximum Load (3) (required, steady) (1) Defined in setion (2) Maintain the airflow nozzle(s) stati pressure differene or veloity pressure during an ON period at the same pressure or veloity as measured during the H0 1 Test. (3) Defined in setion (4) Defined in setion (5) Defined in setion

90 ANSI/ANSI/AHRI STANDARD 210/ Additional test for a heat pump having a heat omfort ontroller. Test any heat pump that has a heat omfort ontroller (see Definition 1.28) aording to setion 3.6.1, 3.6.2, or 3.6.3, whihever applies, with the heat omfort ontroller disabled. Additionally, ondut the abbreviated test desribed in setion with the heat omfort ontroller ative to determine the system's maximum supply air temperature. (Note: heat pumps having a variable speed ompressor and a heat omfort ontroller are not overed in the test proedure at this time.) 3.7 Test proedures for steady-state Maximum Temperature and High Temperature heating mode tests (the H0 1, H1, H1 2, H1 1, and H1 N Tests). a. For the pretest interval, operate the test room reonditioning apparatus and the heat pump until equilibrium onditions are maintained for at least 30 minutes at the speified setion 3.6 test onditions. Use the exhaust fan of the airflow measuring apparatus and, if installed, the indoor fan of the heat pump to obtain and then maintain the indoor air volume rate and/or the external stati pressure speified for the partiular test. Continuously reord the dry-bulb temperature of the air entering the indoor oil, and the dry-bulb temperature and water vapor ontent of the air entering the outdoor oil. Refer to setion 3.11 for additional requirements that depend on the seleted seondary test method. After satisfying the pretest equilibrium requirements, make the measurements speified in Table 3 of ASHRAE Standard (inorporated by referene, see ) for the Indoor Air Enthalpy method and the user-seleted seondary method. Exept for external stati pressure, make the Table 3 measurements at equal intervals that span 10 minutes or less. Measure external stati pressure every 5 minutes or less. Continue data sampling until a 30-minute period (e.g., four onseutive 10-minute samples) is reahed where the test toleranes speified in Table 13 are satisfied. For those ontinuously reorded parameters, use the entire data set for the 30-minute interval when evaluating Table 13 ompliane. Determine the average eletrial power onsumption of the heat pump over the same 30-minute interval. b. Calulate indoor-side total heating apaity as speified in setions and of ASHRAE Standard (inorporated by referene, see ). Do not adjust the parameters used in alulating apaity for the permitted variations in test onditions. Assign the average spae heating apaity and eletrial power over the 30-minute data olletion interval to the variables Q h k and E h k (T) respetively. The T and supersripted k are the same as desribed in setion 3.3. Additionally, for the heating mode, use the supersript to denote results from the optional H1 N Test, if onduted.. For heat pumps tested without an indoor fan installed, inrease Q h k (T) by and inrease E h k (T) by, where V s is the average measured indoor air volume rate expressed in units of ubi feet per minute of standard air (sfm). During the 30-minute data olletion interval of a High Temperature Test, pay attention to preventing a defrost yle. Prior to this time, allow the heat pump to perform a defrost yle if automatially initiated by its own ontrols. As in all ases, wait for the heat pump's defrost ontrols to automatially terminate the defrost yle. Heat pumps that undergo a defrost should operate in the heating mode for at least 10 minutes after defrost termination prior to beginning the 30-minute data olletion interval. For some heat pumps, frost may aumulate on the outdoor oil during a High Temperature test. If the indoor oil leaving air temperature or the differene between the leaving and entering air temperatures dereases by more than 1.5 F over the 30-minute data olletion interval, then do not use the olleted data to determine apaity. Instead, initiate a defrost yle. Begin olleting data no sooner than 10 minutes after defrost termination. Collet 30 minutes of new data during whih the Table 13 test toleranes are satisfied. In this ase, use only the results from the seond 30-minute data olletion interval to evaluate Q h k (47) and E h k (47). 80

91 Indoor dry-bulb, F ANSI/AHRI STANDARD 210/ Table 13. Test Operating and Test Condition Toleranes for Setion 3.7 and Setion 3.10 Steady-State Heating Mode Tests Test Operating Tolerane (1) Test Condition Tolerane (2) Entering temperature... Leaving temperature... Indoor wet-bulb, F Entering temperature... Leaving temperature... Outdoor dry-bulb, F Entering temperature... Leaving temperature... Outdoor wet-bulb, F Entering temperature... Leaving temperature... External resistane to airflow, inhes of water... Eletrial voltage, % of rdg.... Nozzle pressure drop, % of rdg.... Notes: (1) See Definition (2) (3) 0.05 (4) (4) 1.5 (2) See Definition (3) Only applies when the Outdoor Air Enthalpy Method is used. (4) Only applies when testing non-duted units. d. If onduting the optional yli heating mode test, whih is desribed in setion 3.8, reord the average indoor-side air volume rate, V, speifi heat of the air, C p,a (expressed on dry air basis), speifi volume of the air at the nozzles, v n ' (or v n ), humidity ratio at the nozzles, W n, and either pressure differene or veloity pressure for the flow nozzles. If either or both of the below riteria apply, determine the average, steady-state, eletrial power onsumption of the indoor fan motor ( E fan,1): 1. The setion 3.8 yli test will be onduted and the heat pump has a variable-speed indoor fan that is expeted to be disabled during the yli test; or 2. The heat pump has a (variable-speed) onstant-air volume-rate indoor fan and during the steady-state test the average external stati pressure (ΔP 1 ) exeeds the appliable setion minimum (or targeted) external stati pressure (ΔP min ) by 0.03 inhes of water or more. 81

92 ANSI/ANSI/AHRI STANDARD 210/ Determine E fan,1 by making measurements during the 30-minute data olletion interval, or immediately following the test and prior to hanging the test onditions. When the above 2 riteria applies, ondut the following four steps after determining E fan,1 (whih orresponds to ΔP 1 ): i. While maintaining the same test onditions, adjust the exhaust fan of the airflow measuring apparatus until the external stati pressure inreases to approximately ΔP 1 + (ΔP 1 ΔP min ). ii. After re-establishing steady readings for fan motor power and external stati pressure, determine average values for the indoor fan power ( E fan,2) and the external stati pressure (ΔP 2 ) by making measurements over a 5-minute interval. iii. Approximate the average power onsumption of the indoor fan motor if the 30-minute test had been onduted at ΔP min using linear extrapolation: iv. Derease the total spae heating apaity, Q h k (T), by the quantity ( E fan, 1 E fan, min), when expressed on a Btu/h basis. Derease the total eletrial power, E h k (T) by the same fan power differene, now expressed in watts. 3.8 Test proedures for the optional yli heating mode tests (the H0C 1, H1C, H1C 1 and H1C 2 Tests). a. Exept as noted below, ondut the yli heating mode test as speified in setion 3.5. As adapted to the heating mode, replae setion 3.5 referenes to the steady-state dry oil test with the heating mode steady-state test onduted at the same test onditions as the yli heating mode test. Use the test toleranes in Table 14 rather than Table 8. Reord the outdoor oil entering wetbulb temperature aording to the requirements given in setion 3.5 for the outdoor oil entering dry-bulb temperature. Drop the subsript dry used in variables ited in setion 3.5 when referring to quantities from the yli heating mode test. Determine the total spae heating delivered during the yli heating test, q y, as speified in setion 3.5 exept for making the following hanges: (1) When evaluating Equation 3.5 1, use the values of V, C p,a,v n ', (or v n ), and W n that were reorded during the setion 3.7 steady-state test onduted at the same test onditions. (2) Calulate Γ using, b. For duted heat pumps tested without an indoor fan installed (exluding the speial ase where a variable-speed fan is temporarily removed), inrease q y by the amount alulated using Equation Additionally, inrease e y by the amount alulated using Equation In making these alulations, use the average indoor air volume rate ( V s) determined from the setion 3.7 steady-state heating mode test onduted at the same test onditions.. For non-duted heat pumps, subtrat the eletrial energy used by the indoor fan during the 3 minutes after ompressor utoff from the non-duted heat pump's integrated heating apaity, q y. d. If a heat pump defrost yle is manually or automatially initiated immediately prior to or during the OFF/ON yling, operate the heat pump ontinuously until 10 minutes after defrost termination. After that, begin yling the heat pump immediately or delay until the speified test onditions have been re-established. Pay attention to preventing defrosts after beginning the yling proess. For heat pumps that yle off the indoor fan during a defrost yle, make no effort here to restrit the air movement through the indoor oil while the fan is off. Resume the OFF/ON yling while onduting a minimum of two omplete ompressor OFF/ON yles before determining q y and e y Heating mode yli-degradation oeffiient alulation. Use the results from the optional yli test and the required steady-state test that were onduted at the same test onditions to determine the heating-mode yli-degradation oeffiient 82

93 ANSI/AHRI STANDARD 210/ h C D. Add (k=2) to the oeffiient if it orresponds to a two-apaity unit yling at high apaity. For the below alulation of the heating mode yli degradation oeffiient, do not inlude the dut loss orretion from setion of k ASHRAE Standard (inorporated by referene, see ) in determining Q T ) (or q y ). If the optional h ( y h h yli test is onduted but yields a tested C D that exeeds the default C D or if the optional test is not onduted, assign h C D the default value of The default value for two-apaity units yling at high apaity, however, is the low-apaity oeffiient, i.e., C h h h D ( k = 2) = C D. The tested C D is alulated as follows: C h D COPy 1 COPss ( T = 1 HLF y ) where, the average oeffiient of performane during the yli heating mode test, dimensionless. the average oeffiient of performane during the steady-state heating mode test onduted at the same test onditions i.e., same outdoor dry bulb temperature, T y, and speed/apaity, k, if appliable as speified for the yli heating mode test, dimensionless. the heating load fator, dimensionless. T y = the nominal outdoor temperature at whih the yli heating mode test is onduted, 62 or 47 F. Δτ y = the duration of the OFF/ON intervals; 0.5 hours when testing a heat pump having a single-speed or two-apaity ompressor and 1.0 hour when testing a heat pump having a variable-speed ompressor. Round the alulated value for C D h to the nearest If C D h is negative, then set it equal to zero. 83

94 ANSI/ANSI/AHRI STANDARD 210/ Table 14. Test operating and test ondition toleranes for yli heating mode tests Test Operating Tolerane (1) Test Condition Tolerane (2) Indoor entering dry-bulb temperature (3), F Indoor entering wet-bulb temperature (3), F... Outdoor entering dry-bulb temperature (3), F... Outdoor entering wet-bulb temperature (3), F... External resistane to airflow (3), inhes of water... Airflow nozzle pressure differene or veloity pressure (3), % of reading... Eletrial voltage (5), % of rdg.... Notes: (1) See Definition (4) 1.5 (2) See Definition (3) Applies during the interval that air flows through the indoor (outdoor) oil exept for the first 30 seonds after flow initiation. For units having a variable-speed indoor fan that ramps, the toleranes listed for the external resistane to airflow shall apply from 30 seonds after ahieving full speed until ramp down begins. (4) The test ondition shall be the average nozzle pressure differene or veloity pressure measured during the steady-state test onduted at the same test onditions. (5) Applies during the interval that at least one of the following the ompressor, the outdoor fan, or, if appliable, the indoor fan are operating, exept for the first 30 seonds after ompressor start-up. 3.9 Test proedures for Frost Aumulation heating mode tests (the H2, H2 2, H2 V, and H2 1 Tests). a. Confirm that the defrost ontrols of the heat pump are set as speified in setion Operate the test room reonditioning apparatus and the heat pump for at least 30 minutes at the speified setion 3.6 test onditions before starting the preliminary test period. The preliminary test period must immediately preede the offiial test period, whih is the heating and defrost interval over whih data are olleted for evaluating average spae heating apaity and average eletrial power onsumption. b. For heat pumps ontaining defrost ontrols whih are likely to ause defrosts at intervals less than one hour, the preliminary test period starts at the termination of an automati defrost yle and ends at the termination of the next ourring automati defrost yle. For heat pumps ontaining defrost ontrols whih are likely to ause defrosts at intervals exeeding one hour, the preliminary test period must onsist of a heating interval lasting at least one hour followed by a defrost yle that is either manually or automatially initiated. In all ases, the heat pump's own ontrols must govern when a defrost yle terminates.. The offiial test period begins when the preliminary test period ends, at defrost termination. The offiial test period ends at the termination of the next ourring automati defrost yle. When testing a heat pump that uses a time-adaptive defrost ontrol system (see Definition 1.42), however, manually initiate the defrost yle that ends the offiial test period at the instant indiated by instrutions provided by the manufaturer. If the heat pump has not undergone a defrost after 6 hours, immediately onlude the test and use the results from the full 6-hour period to alulate the average spae heating apaity and average eletrial power onsumption. For heat pumps that turn the indoor fan off during the defrost yle, take steps to ease fored airflow through the indoor oil and blok the outlet dut whenever the heat pump's ontrols yle off the indoor fan. If it is installed, use the outlet damper box desribed in setion to affet the bloked outlet dut. 84

95 ANSI/AHRI STANDARD 210/ d. Defrost termination ours when the ontrols of the heat pump atuate the first hange in onverting from defrost operation to normal heating operation. Defrost initiation ours when the ontrols of the heat pump first alter its normal heating operation in order to eliminate possible aumulations of frost on the outdoor oil. e. To onstitute a valid Frost Aumulation test, satisfy the test toleranes speified in Table 15 during both the preliminary and offiial test periods. As noted in Table 15, test operating toleranes are speified for two sub-intervals: (1) When heating, exept for the first 10 minutes after the termination of a defrost yle (Sub-interval H, as desribed in Table 15) and (2) when defrosting, plus these same first 10 minutes after defrost termination (Sub-interval D, as desribed in Table 15). Evaluate ompliane with Table 15 test ondition toleranes and the majority of the test operating toleranes using the averages from measurements reorded only during Sub-interval H. Continuously reord the dry bulb temperature of the air entering the indoor oil, and the dry bulb temperature and water vapor ontent of the air entering the outdoor oil. Sample the remaining parameters listed in Table 15 at equal intervals that span 10 minutes or less. f. For the offiial test period, ollet and use the following data to alulate average spae heating apaity and eletrial power. During heating and defrosting intervals when the ontrols of the heat pump have the indoor fan on, ontinuously reord the dry-bulb temperature of the air entering (as noted above) and leaving the indoor oil. If using a thermopile, ontinuously reord the differene between the leaving and entering dry-bulb temperatures during the interval(s) that air flows through the indoor oil. For heat pumps tested without an indoor fan installed, determine the orresponding umulative time (in hours) of indoor oil airflow, Δτ a. Sample measurements used in alulating the air volume rate (refer to setions and of ASHRAE Standard (inorporated by referene, see )) at equal intervals that span 10 minutes or less. (Note: In the first printing of ASHRAE Standard , the seond IP equation for Q mi should read: 1097 CAn P V ν n.). Reord the eletrial energy onsumed, expressed in watt-hours, from defrost termination to defrost termination, e k DEF (35), as well as the orresponding elapsed time in hours, Δτ FR Average spae heating apaity and eletrial power alulations. a. Evaluate average spae heating apaity, Q h k (35), when expressed in units of Btu per hour, using: where, V = the average indoor air volume rate measured during Sub-interval H, fm. C p, a = W n, the onstant pressure speifi heat of the air-water vapor mixture that flows through the indoor oil and is expressed on a dry air basis, Btu / lbm da F. v n ' = speifi volume of the air-water vapor mixture at the nozzle, ft 3 / lbm mx. 85

96 ANSI/ANSI/AHRI STANDARD 210/ Table 15. Test Operating and Test Condition Toleranes for Frost Aumulation Heating Mode Tests Indoor entering dry-bulb temperature, F... Test Operating Tolerane (1) Test ondition (2) Sub-interval tolerane H(3) Sub-interval D (4) Sub-interval H (3) (5) 0.5 Indoor entering wet-bulb temperature, F Outdoor entering dry-bulb temperature, F Outdoor entering wet-bulb temperature, F External resistane to airflow, inhes of water (6) Eletrial voltage, % of rdg Notes: (1) See Definition (2) See Definition (3) Applies when the heat pump is in the heating mode, exept for the first 10 minutes after termination of a defrost yle. (4) Applies during a defrost yle and during the first 10 minutes after the termination of a defrost yle when the heat pump is operating in the heating mode. (5) For heat pumps that turn off the indoor fan during the defrost yle, the noted tolerane only applies during the 10 minute interval that follows defrost termination. (6) Only applies when testing non-duted heat pumps. W n = humidity ratio of the air-water vapor mixture at the nozzle, lbm of water vapor per lbm of dry air. Δτ FR = τ 2 τ 1, the elapsed time from defrost termination to defrost termination, hr. T al (τ) = dry bulb temperature of the air entering the indoor oil at elapsed time τ, F; only reorded when indoor oil airflow ours; assigned the value of zero during periods (if any) where the indoor fan yles off. T a2 (τ) = dry bulb temperature of the air leaving the indoor oil at elapsed time τ, F; only reorded when indoor oil airflow ours; assigned the value of zero during periods (if any) where the indoor fan yles off. τ 1 = the elapsed time when the defrost termination ours that begins the offiial test period, hr. τ 2 = the elapsed time when the next automatially ourring defrost termination ours, thus ending the offiial test period, hr. v n = speifi volume of the dry air portion of the mixture evaluated at the dry-bulb temperature, vapor ontent, and barometri pressure existing at the nozzle, ft 3 per lbm of dry air. 86

97 ANSI/AHRI STANDARD 210/ To aount for the effet of dut losses between the outlet of the indoor unit and the setion dry-bulb temperature grid, adjust (35) in aordane with setion of ASHRAE Standard (inorporated by referene, see ). Q k h b. Evaluate average eletrial power, E h k (35), when expressed in units of watts, using: For heat pumps tested without an indoor fan installed, inrease Q h k (35) by, and inrease E h k (35) by, where V s is the average indoor air volume rate measured during the Frost Aumulation heating mode test and is expressed in units of ubi feet per minute of standard air (sfm).. For heat pumps having a onstant-air-volume-rate indoor fan, the five additional steps listed below are required if the average of the external stati pressures measured during sub-interval H exeeds the appliable setion , , or minimum (or targeted) external stati pressure (ΔP min ) by 0.03 inhes of water or more: 1. Measure the average power onsumption of the indoor fan motor ( E fan,1) and reord the orresponding external stati pressure (ΔP 1 ) during or immediately following the Frost Aumulation heating mode test. Make the measurement at a time when the heat pump is heating, exept for the first 10 minutes after the termination of a defrost yle. 2. After the Frost Aumulation heating mode test is ompleted and while maintaining the same test onditions, adjust the exhaust fan of the airflow measuring apparatus until the external stati pressure inreases to approximately ΔP 1 + (ΔP 1 ΔP min ). 3. After re-establishing steady readings for the fan motor power and external stati pressure, determine average values for the indoor fan power ( E fan,2) and the external stati pressure (ΔP 2 ) by making measurements over a 5-minute interval. 4. Approximate the average power onsumption of the indoor fan motor had the Frost Aumulation heating mode test been onduted at ΔP min using linear extrapolation: 5. Derease the total heating apaity, Q h k (35), by the quantity [( E fan, 1 E fan, min) (Δτ a /Δτ FR ], when expressed on a Btu/h basis. Derease the total eletrial power, E h k (35), by the same quantity, now expressed in watts Demand defrost redit. a. Assign the demand defrost redit, F def, that is used in setion 4.2 to the value of 1 in all ases exept for heat pumps having a demand-defrost ontrol system (Definition 1.21). For suh qualifying heat pumps, evaluate F def using, 87

98 ANSI/ANSI/AHRI STANDARD 210/ where, Δτ def = the time between defrost terminations (in hours) or 1.5, whihever is greater. Δτ max = maximum time between defrosts as allowed by the ontrols (in hours) or 12, whihever is less. b. For two-apaity heat pumps and for setion units, evaluate the above equation using the Δτ def that applies based on the Frost Aumulation Test onduted at high apaity and/or at the Heating Full-load Air Volume Rate. For variable-speed heat pumps, evaluate Δτ def based on the required Frost Aumulation Test onduted at the intermediate ompressor speed Test proedures for steady-state Low Temperature heating mode tests (the H3, H3 2, and H3 1 Tests). Exept for the modifiations noted in this setion, ondut the Low Temperature heating mode test using the same approah as speified in setion 3.7 for the Maximum and High Temperature tests. After satisfying the setion 3.7 requirements for the pretest interval but before beginning to ollet data to determine Q h k (17) and E h k (17), ondut a defrost yle. This defrost yle may be manually or automatially initiated. The defrost sequene must be terminated by the ation of the heat pump's defrost ontrols. Begin the 30-minute data olletion interval desribed in setion 3.7, from whih Q h k (17) and E h k (17) are determined, no sooner than 10 minutes after defrost termination. Defrosts should be prevented over the 30-minute data olletion interval Additional requirements for the seondary test methods If using the Outdoor Air Enthalpy Method as the seondary test method. During the offiial test, the outdoor airside test apparatus desribed in setion is onneted to the outdoor unit. To help ompensate for any effet that the addition of this test apparatus may have on the unit's performane, ondut a preliminary test where the outdoor air-side test apparatus is disonneted. Condut a preliminary test prior to the first setion 3.2 steady-state ooling mode test and prior to the first setion 3.6 steady-state heating mode test. No other preliminary tests are required so long as the unit operates the outdoor fan during all ooling mode steady-state tests at the same speed and all heating mode steady-state tests at the same speed. If using more than one outdoor fan speed for the ooling mode steady-state tests, however, ondut a preliminary test prior to eah ooling mode test where a different fan speed is first used. This same requirement applies for the heating mode tests If a preliminary test preedes the offiial test. a. The test onditions for the preliminary test are the same as speified for the offiial test. Connet the indoor air-side test apparatus to the indoor oil; disonnet the outdoor air-side test apparatus. Allow the test room reonditioning apparatus and the unit being tested to operate for at least one hour. After attaining equilibrium onditions, measure the following quantities at equal intervals that span 10 minutes or less: 1. The setion evaporator and ondenser temperatures or pressures; 2. Parameters required aording to the Indoor Air Enthalpy Method. Continue these measurements until a 30-minute period (e.g., four onseutive 10-minute samples) is obtained where the Table 7 or Table 13, whihever applies, test toleranes are satisfied. b. After olleting 30 minutes of steady-state data, reonnet the outdoor air-side test apparatus to the unit. Adjust the exhaust fan of the outdoor airflow measuring apparatus until averages for the evaporator and ondenser temperatures, or the saturated temperatures orresponding to the measured pressures, agree within ±0.5 F of the averages ahieved when the outdoor airside test apparatus was disonneted. Calulate the averages for the reonneted ase using five or more onseutive readings taken at one minute intervals. Make these onseutive readings after re-establishing equilibrium onditions and before initiating the offiial test If a preliminary test does not preede the offiial test. Connet the outdoor-side test apparatus to the unit. Adjust the exhaust fan of the outdoor airflow measuring apparatus to ahieve the same external stati pressure as measured during the prior preliminary test onduted with the unit operating in the same ooling or heating mode at the same outdoor fan speed. 88

99 ANSI/AHRI STANDARD 210/ Offiial test. a. Continue (preliminary test was onduted) or begin (no preliminary test) the offiial test by making measurements for both the Indoor and Outdoor Air Enthalpy Methods at equal intervals that span 10 minutes or less. Disontinue these measurement only after obtaining a 30-minute period where the speified test ondition and test operating toleranes are satisfied. To onstitute a valid offiial test: (1) Ahieve the energy balane speified in setion 3.1.1; and, (2) For ases where a preliminary test is onduted, the apaities determined using the Indoor Air Enthalpy Method from the offiial and preliminary test periods must agree within 2.0 perent. b. For spae ooling tests, alulate apaity from the outdoor air-enthalpy measurements as speified in setions and of ASHRAE Standard (inorporated by referene, see ). Calulate heating apaity based on outdoor air-enthalpy measurements as speified in setions and of the same ASHRAE Standard. Adjust the outdoorside apaity aording to setion of ASHRAE Standard (inorporated by referene, see ) to aount for line losses when testing split systems. Use the outdoor unit fan power as measured during the offiial test and not the value measured during the preliminary test, as desribed in setion of ASHRAE Standard (inorporated by referene, see ), when alulating the apaity If using the Compressor Calibration Method as the seondary test method. a. Condut separate alibration tests using a alorimeter to determine the refrigerant flow rate. Or for ases where the superheat of the refrigerant leaving the evaporator is less than 5 F, use the alorimeter to measure total apaity rather than refrigerant flow rate. Condut these alibration tests at the same test onditions as speified for the tests in this Appendix. Operate the unit for at least one hour or until obtaining equilibrium onditions before olleting data that will be used in determining the average refrigerant flow rate or total apaity. Sample the data at equal intervals that span 10 minutes or less. Determine average flow rate or average apaity from data sampled over a 30-minute period where the Table 7 (ooling) or the Table 13 (heating) toleranes are satisfied. Otherwise, ondut the alibration tests aording to ASHRAE Standard (inorporated by referene, see ), ASHRAE Standard (inorporated by referene, see ), and setion 7.4 of ASHRAE Standard (inorporated by referene, see ). b. Calulate spae ooling and spae heating apaities using the ompressor alibration method measurements as speified in setion and respetively, of ASHRAE Standard (inorporated by referene, see ) If using the Refrigerant-Enthalpy Method as the seondary test method. Condut this seondary method aording to setion 7.5 of ASHRAE Standard (inorporated by referene, see ). Calulate spae ooling and heating apaities using the refrigerant-enthalpy method measurements as speified in setions and 7.5.5, respetively, of the same ASHRAE Standard Rounding of spae onditioning apaities for reporting purposes. a. When reporting rated apaities, round them off as follows: 1. For apaities less than 20,000 Btu/h, round to the nearest 100 Btu/h. 2. For apaities between 20,000 and 37,999 Btu/h, round to the nearest 200 Btu/h. 3. For apaities between 38,000 and 64,999 Btu/h, round to the nearest 500 Btu/h. b. For the apaities used to perform the setion 4 alulations, however, round only to the nearest integer. 89

100 ANSI/ANSI/AHRI STANDARD 210/ CALCULATIONS OF SEASONAL PERFORMANCE DESCRIPTORS 4.1 Seasonal Energy Effiieny Ratio (SEER) Calulations. SEER must be alulated as follows: For equipment overed under setions 4.1.2, 4.1.3, and 4.1.4, evaluate the seasonal energy effiieny ratio, where, the ratio of the total spae ooling provided during periods of the spae ooling season when the outdoor temperature fell within the range represented by bin temperature T j to the total number of hours in the ooling season (N), Btu/h. the eletrial energy onsumed by the test unit during periods of the spae ooling season when the outdoor temperature fell within the range represented by bin temperature T j to the total number of hours in the ooling season (N), W. T j = the outdoor bin temperature, F. Outdoor temperatures are grouped or binned. Use bins of 5 F with the 8 ooling season bin temperatures being 67, 72, 77, 82, 87, 92, 97, and 102 F. j = the bin number. For ooling season alulations, j ranges from 1 to 8. Additionally, for setions 4.1.2, 4.1.3, and 4.1.4, use a building ooling load, BL (T j ). When referened, evaluate BL(T j ) for ooling using, where, Q k=2 (95) = the spae ooling apaity determined from the A 2 Test and alulated as speified in setion 3.3, Btu/h. 1.1 = sizing fator, dimensionless. The temperatures 95 F and 65 F in the building load equation represent the seleted outdoor design temperature and the zero-load base temperature, respetively SEER alulations for an air onditioner or heat pump having a single-speed ompressor that was tested with a fixedspeed indoor fan installed, a onstant-air-volume-rate indoor fan installed, or with no indoor fan installed. a. Evaluate the seasonal energy effiieny ratio, expressed in units of Btu/watt-hour, using: SEER = PLF(0.5) EER B 90

101 ANSI/AHRI STANDARD 210/ where, the energy effiieny ratio determined from the B Test desribed in setions 3.2.1, , and 3.3, Btu/h per watt. PLF (0.5) = C D, the part-load performane fator evaluated at a ooling load fator of 0.5, dimensionless. b. Refer to setion 3.3 regarding the definition and alulation of Q (82) and E (82). If the optional tests desribed in setion are not onduted, set the ooling mode yli degradation oeffiient, C D, to the default value speified in setion If these optional tests are onduted, set C D to the lower of: 1. The value alulated as per setion 3.5.3; or 2. The setion default value of SEER alulations for an air onditioner or heat pump having a single-speed ompressor and a variable-speed variable-air-volume-rate indoor fan Units overed by setion where indoor fan apaity modulation orrelates with the outdoor dry bulb temperature. The manufaturer must provide information on how the indoor air volume rate or the indoor fan speed varies over the outdoor temperature range of 67 F to 102 F. Calulate SEER using Equation Evaluate the quantity q (T j )/N in Equation using, where, whihever is less; the ooling mode load fator for temperature bin j, dimensionless. Q (T j ) = the spae ooling apaity of the test unit when operating at outdoor temperature, T j, Btu/h. n j /N = frational bin hours for the ooling season; the ratio of the number of hours during the ooling season when the outdoor temperature fell within the range represented by bin temperature T j to the total number of hours in the ooling season, dimensionless. a. For the spae ooling season, assign n j /N as speified in Table 16. Use Equation to alulate the building load, BL (T j ). Evaluate Q (T j ) using, where, 91

102 ANSI/ANSI/AHRI STANDARD 210/ the spae ooling apaity of the test unit at outdoor temperature T j if operated at the Cooling Minimum Air Volume Rate, Btu/h. the spae ooling apaity of the test unit at outdoor temperature T j if operated at the Cooling Full-load Air Volume Rate, Btu/h. b. For units where indoor fan speed is the primary ontrol variable, FP k=1 denotes the fan speed used during the required A 1 and B 1 Tests (see setion ), FP k=2 denotes the fan speed used during the required A 2 and B 2 Tests, and FP (T j ) denotes the fan speed used by the unit when the outdoor temperature equals T j. For units where indoor air volume rate is the primary ontrol variable, the three FP 's are similarly defined only now being expressed in terms of air volume rates rather than fan speeds. Refer to setions , to , and 3.3 regarding the definitions and alulations of Q k=1 (82), Q k=1 (95), Q k=2 (82), and Q k=2 (95). Calulate e (T j )/N in Equation using, where, PLF j = 1 C D [1 X (T j )], the part load fator, dimensionless. E (T j ) = the eletrial power onsumption of the test unit when operating at outdoor temperature T j, W.. The quantities X (T j ) and n j /N are the same quantities as used in Equation If the optional tests desribed in setion and Table 4 are not onduted, set the ooling mode yli degradation oeffiient, C D, to the default value speified in setion If these optional tests are onduted, set C D to the lower of: 1. The value alulated as per setion 3.5.3; or 2. The setion default value of d. Evaluate E (T j ) using, where the eletrial power onsumption of the test unit at outdoor temperature T j if operated at the Cooling Minimum Air Volume Rate, W. 92

103 ANSI/AHRI STANDARD 210/ the eletrial power onsumption of the test unit at outdoor temperature T j if operated at the Cooling Full-load Air Volume Rate, W. e. The parameters FP k=1, and FP k=2, and FP (T j ) are the same quantities that are used when evaluating Equation Refer to setions , to , and 3.3 regarding the definitions and alulations of E k=1 (82), E k=1 (95), E k=2 (82), and E k=2 (95) Units overed by setion where indoor fan apaity modulation is used to adjust the sensible to total ooling apaity ratio. Calulate SEER as speified in setion SEER alulations for an air onditioner or heat pump having a two-apaity ompressor. Calulate SEER using k Equation Evaluate the spae ooling apaity, Q = 1 ( T j ), and eletrial power onsumption, k E = 1 ( ) T j, of the test unit when operating at low ompressor apaity and outdoor temperature T j using, Q Q ( 67) + k ( 82) Q ( 67 k = 1 = 1 k = 1 k = 1 ) ( T j ) = Q ( T 67) ( ) j ( T 67) E 82 E 67 E k = 1 k = 1 k = 1 k = 1 ( ) ( ) ( T j ) = E ( 67) + j ( ) where Q k = 1 (82) and E k = 1 (82) are determined from the B 1 Test, Q k = 1 (67) and E k = 1 (67) are determined from the F 1 k Test, and all four quantities are alulated as speified in setion 3.3. Evaluate the spae ooling apaity, Q = 2 ( Tj ), and k eletrial power onsumption, E = 2 ( Tj ), of the test unit when operating at high ompressor apaity and outdoor temperature T j using, Q k= 2 k= 2 k= 2 k= 2 ( 95) Q 82 Q ( ) ( T j ) = Q ( 82) + ( T j 82) ( ) where Q k=2 (95) and E k=2 (95) are determined from the A 2 Test, Q k=2 (82), and E k=2 (82), are determined from the B 2 Test, and all are alulated as speified in setion 3.3. The alulation of Equation quantities q (T j )/N and e (T j )/N differs depending on whether the test unit would operate at low apaity (setion ), yle between low and high apaity (setion ), or operate at high apaity (setions and ) in responding to the building load. For units that lok out low apaity operation at higher outdoor temperatures, the manufaturer must supply information regarding this temperature so that the appropriate equations are used. Use Equation to alulate the building load, BL (T j ), for eah temperature bin Steady-state spae ooling apaity at low ompressor apaity is greater than or equal to the building ooling load at temperature T j, Q k=1 (T j ) BL(T j ). 93

104 ANSI/ANSI/AHRI STANDARD 210/ where, X k=1 (T j ) = BL (T j )/ Q k=1 (T j ), the ooling mode low apaity load fator for temperature bin j, dimensionless. PLF j = 1 C D [1 X k=1 (T j )], the part load fator, dimensionless. frational bin hours for the ooling season; the ratio of the number of hours during the ooling season when the outdoor temperature fell within the range represented by bin temperature T j to the total number of hours in the ooling season, dimensionless. Obtain the frational bin hours for the ooling season, n j /N, from Table 16. Use Equations and , respetively, to evaluate Q k=1 (T j ) and E k=1 (T j ). If the optional tests desribed in setion and Table 5 are not onduted, set the ooling mode yli degradation oeffiient, C D, to the default value speified in setion If these optional tests are onduted, set C D to the lower of: a. The value alulated aording to setion 3.5.3; or b. The setion default value of Unit alternates between high (k=2) and low (k=1) ompressor apaity to satisfy the building ooling load at temperature T j, Q k=1 (T j ) < BL (T j ) < Q k=2 (T j ). where, the ooling mode, low apaity load fator for temperature bin j, dimensionless. X k=2 (T j ) = 1 X k=1 (T j ), the ooling mode, high apaity load fator for temperature bin j, dimensionless. Obtain the frational bin hours for the ooling season, n j /N, from Table 16. Use Equations and , respetively, to evaluate Q k=1 (T j ) and E k=1 (T j ). Use Equations and , respetively, to evaluate Q k=2 (T j ) and E k=2 (T j ). 94

105 ANSI/AHRI STANDARD 210/ Unit only operates at high (k=2) ompressor apaity at temperature T j and its apaity is greater than the building ooling load, BL (T j ) < Q k=2 (T j ). This setion applies to units that lok out low ompressor apaity operation at higher outdoor temperatures. Table 16. Distribution of Frational Hours Within Cooling Season Temperature Bins Bin Number, j 1... Bin Temperature Range F Representative Temperature for bin F 67 Fration of Total Temperature Bin Hours, N j /N where, X k=2 (T j ) = BL (T j )/ Q k=2 (T j ), the ooling mode high apaity load fator for temperature bin j, dimensionless. PLF j k = 2 = 1 C k = 2) [ 1 X ( T )], the part load fator, dimensionless. D ( j Obtain the fration bin hours for the ooling season, N n j, from Table 16. Use Equations and , respetively, to k 2 evaluate Q = ( T j ) and k 2 E = ( ) T j. If the optional C 2 and D 2 Tests desribed in setion and Table 5 are not onduted, set C D (k=2) equal to the default value speified in setion If these optional tests are onduted, set C D ( k = 2) to the lower of: a. the ( k 2) C D = value alulated as per setion 3.5.3; or b. the setion default value for ( k 2) C D =. 95

106 ANSI/ANSI/AHRI STANDARD 210/ Unit must operate ontinuously at high (k=2) ompressor apaity at temperature T j, BL (T j ) Q k=2 (T j ). Obtain the frational bin hours for the ooling season, n j /N, from Table 16. Use Equations and , respetively, to evaluate Q k=2 (T j ) and E k=2 (T j ) SEER alulations for an air onditioner or heat pump having a variable-speed ompressor. Calulate SEER using k Equation Evaluate the spae ooling apaity, Q = 1 ( T ), and eletrial power onsumption, k E = 1 ( T ), of the test unit when operating at minimum ompressor speed and outdoor temperature T j. Use Equations and , respetively, where Q = 1 (82) and E = 1 (82) are determined from the B 1 Test, Q = 1 (67) and E = 1 (67) are k k determined from the F 1 Test, and all four quantities are alulated as speified in setion 3.3. Evaluate the spae ooling k 2 apaity, Q = T ), and eletrial power onsumption, ( j k 2 ( T ), of the test unit when operating at maximum ompressor speed and outdoor temperature T. Use Equations j E = j 3 and , respetively, where Q k =2 (95) and E k =2 (95) are determined from the A 2 Test, Q k =2 (82) and E k =2 (82) are determined from the B 2 Test, and all four quantities are alulated as speified in setion 3.3. Calulate the spae ooling k v apaity, Q = T ), and eletrial power onsumption, k v E = T ), of the test unit when operating at outdoor temperature ( j T j and the intermediate ompressor speed used during the setion (and Table 6) E V Test using, ( T 87) Q k= v k= v ( T ) = Q ( 87) + M ( ) j Q j ( T 87) E k= v k= v ( T ) = E ( 87) + M ( ) j E j where Q k = v (87) and E k = v (87 ) are determined from the E V Test and alulated as speified in setion 3.3. Approximate the slopes of the k = v intermediate speed ooling apaity and eletrial power input urves, M Q and M E, as follows: j ( j k j k where, k = v k = 1 Q (87) Q (87) NQ =, and k = 2 k = 1 Q (87) Q (87) determine Q k = 1 (87) and E k = 1 (87) Q = 2 (87) and E = 2 (87) k k, respetively. Calulating Equation quantities E = E ( 87) E ( 87) E k= v k= 1 N E k= 2 k= 1 q ( 87) ( 87). Use Equations and for T j = 87 F to, respetively. Use Equations and for T j = 87 F to determine ( T ) N j ( ) e Tj and N differs depending upon whether the test unit would operate at 96

107 ANSI/AHRI STANDARD 210/ minimum speed (setion ), operate at an intermediate speed (setion ), or operate at maximum speed (setion ) in responding to the building load. Use Equation to alulate the building load, BL(T j ), for eah temperature bin Steady-state spae ooling apaity when operating at minimum ompressor speed is greater than or equal to the building ooling load at temperature T j, Q k=1 (T j ) BL(T j ). where, X k=1 (T j ) = BL (T j ) / Q k=1 (T j ), the ooling mode minimum speed load fator for temperature bin j, dimensionless. PLF j = 1 C D [1 X k=1 (T j )], the part load fator, dimensionless. n j /N = frational bin hours for the ooling season; the ratio of the number of hours during the ooling season when the outdoor temperature fell within the range represented by bin temperature T j to the total number of hours in the ooling season, dimensionless. Obtain the frational bin hours for the ooling season, n j /N, from Table 16. Use Equations and , respetively, to evaluate k 1 Q = ( T j ) and k 1 E = ( ) T j. If the optional tests desribed in setion and Table 6. If the optional tests desribed in setion and Table 6 are not onduted, set the ooling mode yli degradation oeffiient, C D, to the default value speified in setion If these optional tests are onduted, set C D to the lower of: a. The value alulated aording to setion 3.5.3; or b. The setion default value of Unit operates at an intermediate ompressor speed (k=i) in order to math the building ooling load at temperature T j, Q k=1 (T j ) < BL (T j ) < Q k=2 (T j ). where, Q k=i (T j ) = BL (T j ), the spae ooling apaity delivered by the unit in mathing the building load at temperature T j, Btu/h. The mathing ours with the unit operating at ompressor speed k = i. the eletrial power input required by the test unit when operating at a ompressor speed of k = i and temperature T j, W. EER k=i (T j ) = the steady-state energy effiieny ratio of the test unit when operating at a ompressor speed of k = i and temperature T j, Btu/h per W. Obtain the frational bin hours for the ooling season, n j /N, from Table 16. For eah temperature bin where the unit operates at an intermediate ompressor speed, determine the energy effiieny ratio EER k=i (T j ) using, 97

108 ANSI/ANSI/AHRI STANDARD 210/ EER k=i (T j ) = A + B T j + C T j 2. For eah unit, determine the oeffiients A, B, and C by onduting the following alulations one: A = EER k= 2 ( T ) B T 2 2 C T 2 2 where, T 1 = the outdoor temperature at whih the unit, when operating at minimum ompressor speed, provides a spae ooling k 1 apaity that is equal to the building load ( Q = ( T1 ) = BL( T1 ) ), F. Determine T 1 by equating Equations and and solving for outdoor temperature. T v = the outdoor temperature at whih the unit, when operating at the intermediate ompressor speed used during the setion k v E V Test, provides a spae ooling apaity that is equal to the building load ( Q = ( Tv ) = BL( Tv ) ), F. Determine T v by equating Equations and and solving for outdoor temperature. EER EER k = 1 Q ( T1 ) = E Q = k = 1 k = 1 k = v k = v ( Tv ) k = v E ( T ) 1 ( T ) 1 ( T ) v ( T ) v [ Eqn , substituting T1 for Tj ] [ Eqn , substituting T for T ] [ Eqn , substituting Tv for Tj ] [ Eqn , substituting T for T ] 1 v j j, Btu/h per W., Btu/h per W. For multiple-split air onditioners and heat pumps (only), the following proedures supersede the above requirements for k i alulating EER = T ). For eah temperature bin where T 1 < T j < T v, EER k= i ( j k= v k= 1 k= 1 EER ( Tv ) EER ( T1 ) ( T j ) = EER ( T1 ) + ( T j T1 ). T T v Unit must operate ontinuously at maximum (k=2) ompressor speed at temperature Tj, BL (T j ) Q k=2 (T j ). Evaluate the Equation quantities as speified in setion with the understanding that Q k=2 (T j ) and E k=2 (T j ) orrespond to maximum ompressor speed operation and are derived from the results of the tests speified in setion Heating Seasonal Performane Fator (HSPF) Calulations. Unless an approved alternative rating method is used, as set forth in 10 CFR (m), Subpart B, HSPF must be alulated as follows: Six generalized limati regions are depited in Figure 2 and otherwise defined in Table 17. For eah of these regions and for eah appliable standardized design heating requirement, evaluate the heating seasonal performane fator using, 98

109 ANSI/AHRI STANDARD 210/ where, e h (T j )/N= The ratio of the eletrial energy onsumed by the heat pump during periods of the spae heating season when the outdoor temperature fell within the range represented by bin temperature T j to the total number of hours in the heating season (N), W. For heat pumps having a heat omfort ontroller, this ratio may also inlude eletrial energy used by resistive elements to maintain a minimum air delivery temperature (see 4.2.5). RH(T j )/N= The ratio of the eletrial energy used for resistive spae heating during periods when the outdoor temperature fell within the range represented by bin temperature T j to the total number of hours in the heating season (N),W. Exept as noted in setion 4.2.5, resistive spae heating is modeled as being used to meet that portion of the building load that the heat pump does not meet beause of insuffiient apaity or beause the heat pump automatially turns off at the lowest outdoor temperatures. For heat pumps having a heat omfort ontroller, all or part of the eletrial energy used by resistive heaters at a partiular bin temperature may be refleted in e h (T j )/N (see 4.2.5). T j = the outdoor bin temperature, F. Outdoor temperatures are binned suh that alulations are only performed based one temperature within the bin. Bins of 5 F are used. n j /N= Frational bin hours for the heating season; the ratio of the number of hours during the heating season when the outdoor temperature fell within the range represented by bin temperature T j to the total number of hours in the heating season, dimensionless. Obtain n j /N values from Table 17. j = the bin number, dimensionless. J = for eah generalized limati region, the total number of temperature bins, dimensionless. Referring to Table 17, J is the highest bin number (j) having a nonzero entry for the frational bin hours for the generalized limati region of interest. F def = the demand defrost redit desribed in setion 3.9.2, dimensionless. BL(T j ) = the building spae onditioning load orresponding to an outdoor temperature of T j ; the heating season building load also depends on the generalized limati region's outdoor design temperature and the design heating requirement, Btu/h. 99

110 ANSI/ANSI/AHRI STANDARD 210/ Table 17. Generalized Climati Region Information Region Number... I II III IV V VI Heating Load Hours, HLH *2750 Outdoor Design Temperature, T OD j Tj ( F)... Frational Bin Hours n j /N * Paifi Coast Region. Evaluate the building heating load using where, T OD = the outdoor design temperature, F. An outdoor design temperature is speified for eah generalized limati region in Table

111 ANSI/AHRI STANDARD 210/ C = 0.77, a orretion fator whih tends to improve the agreement between alulated and measured building loads, dimensionless. DHR = the design heating requirement (see Definition 1.22), Btu/h. Calulate the minimum and maximum design heating requirements for eah generalized limati region as follows: and where Q h k (47) is expressed in units of Btu/h and otherwise defined as follows: 1. For a single-speed heat pump tested as per setion 3.6.1, Q h k (47) = Q h (47), the spae heating apaity determined from the H1 Test. 2. For a variable-speed heat pump, a setion single-speed heat pump, or a two-apaity heat pump not overed by item 3, Q n k (47) = Q n k=2 (47), the spae heating apaity determined from the H1 2 Test. 3. For two-apaity, northern heat pumps (see Definition 1.46), Q k h (47) = Q k=1 h (47), the spae heating apaity determined from the H1 1 Test. If the optional H1 N Test is onduted on a variable-speed heat pump, the manufaturer has the option of defining Q k h (47) as speified above in item 2 or as Q k h (47)= Q k=n h (47), the spae heating apaity determined from the H1 N Test. For all heat pumps, HSPF aounts for the heating delivered and the energy onsumed by auxiliary resistive elements when operating below the balane point. This ondition ours when the building load exeeds the spae heating apaity of the heat pump ondenser. For HSPF alulations for all heat pumps, see either setion 4.2.1, 4.2.2, 4.2.3, or 4.2.4, whihever applies. Table 18. Standardized Design Heating Requirements (Btu/h) 5, ,000 50,000 90,000 10, ,000 60, ,000 15, ,000 70, ,000 20, ,000 80, ,

112 ANSI/ANSI/AHRI STANDARD 210/ For heat pumps with heat omfort ontrollers (see Definition 1.28), HSPF also aounts for resistive heating ontributed when operating above the heat-pump-plus-omfort-ontroller balane point as a result of maintaining a minimum supply temperature. For heat pumps having a heat omfort ontroller, see setion for the additional steps required for alulating the HSPF Additional steps for alulating the HSPF of a heat pump having a single-speed ompressor that was tested with a fixed-speed indoor fan installed, a onstant-air-volume-rate indoor fan installed, or with no indoor fan installed. where, whihever is less; the heating mode load fator for temperature bin j, dimensionless. Q h (T j ) = the spae heating apaity of the heat pump when operating at outdoor temperature T j, Btu/h. E h (T j ) = the eletrial power onsumption of the heat pump when operating at outdoor temperature T j, W. δ (T j ) = the heat pump low temperature ut-out fator, dimensionless. PLF j = 1 C Dh [1 X (T j )] the part load fator, dimensionless. Use Equation to determine BL (T j ). Obtain frational bin hours for the heating season, n j /N, from Table 17. If the optional H1C Test desribed in setion is not onduted, set the heating mode yli degradation oeffiient, C D h, to the default value speified in setion If this optional test is onduted, set C D h to the lower of: a. The value alulated aording to setion or b. The setion default value of Determine the low temperature ut-out fator using 102

113 ANSI/AHRI STANDARD 210/ where, T off = the outdoor temperature when the ompressor is automatially shut off, F. (If no suh temperature exists, T j is always greater than T off and T on ). T on = the outdoor temperature when the ompressor is automatially turned bak on, if appliable, following an automati shut-off, F. Calulate Q h(t j ) and E h(t j ) using, where Q h (47) and E h (47) are determined from the H1 Test and alulated as speified in setion 3.7; Q h (35) and E h (35) are determined from the H2 Test and alulated as speified in setion 3.9.1; and Q h (17) and E h (17) are determined from the H3 Test and alulated as speified in setion Additional steps for alulating the HSPF of a heat pump having a single-speed ompressor and a variable-speed, variable-air-volume-rate indoor fan. The manufaturer must provide information about how the indoor air volume rate or the indoor fan speed varies over the outdoor temperature range of 65 F to 23 F. Calulate the quantities in Equation as speified in setion with the exeption of replaing referenes to the H1C Test and setion with the H1C 1 Test and setion In addition, evaluate the spae heating apaity and eletrial power onsumption of the heat pump Q h(t j ) and E h(t j ) using where the spae heating apaity and eletrial power onsumption at both low apaity (k=1) and high apaity (k=2) at outdoor temperature Tj are determined using 103

114 ANSI/ANSI/AHRI STANDARD 210/ For units where indoor fan speed is the primary ontrol variable, FP k=1 h denotes the fan speed used during the required H1 1 and H3 1 Tests (see Table 10), FP k=2 h denotes the fan speed used during the required H1 2, H2 2, and H3 2 Tests, and FP h (T j ) denotes the fan speed used by the unit when the outdoor temperature equals T j. For units where indoor air volume rate is the primary ontrol variable, the three FP h 's are similarly defined only now being expressed in terms of air volume rates rather than fan speeds. Determine Q h k=1 (47) and E h k=1 (47) from the H1 1 Test, and Q h k=2 (47) and E h k=2 (47) from the H1 2 Test. Calulate all four quantities as speified in setion 3.7. Determine Q h k=1 (35) and E h k=1 (35) as speified in setion 3.6.2; determine Q h k=2 (35) and E h k=2 (35) and from the H2 2 Test and the alulation speified in setion 3.9. Determine Q h k=1 (17) and E h k=1 (17 from the H3 1 Test, and Q h k=2 (17) and E h k=2 (17) from the H3 2 Test. Calulate all four quantities as speified in setion Additional steps for alulating the HSPF of a heat pump having a two-apaity ompressor. The alulation of the Equation quantities differs depending upon whether the heat pump would operate at low apaity (setion ), yle between low and high apaity (Setion ), or operate at high apaity (setions and ) in responding to the building load. For heat pumps that lok out low apaity operation at low outdoor temperatures, the manufaturer must supply information regarding the utoff temperature(s) so that the appropriate equations an be seleted. a. Evaluate the spae heating apaity and eletrial power onsumption of the heat pump when operating at low ompressor apaity and outdoor temperature T j using 104

115 ANSI/AHRI STANDARD 210/ b. Evaluate the spae heating apaity and eletrial power onsumption ( Q h k=2 (T j ) and E h k=2 (T j )) of the heat pump when operating at high ompressor apaity and outdoor temperature Tj by solving Equations and , respetively, for k=2. Determine Q h k=1 (62) and E h k=1 (62) from the H0 1 Test, Q h k=1 (47) and E h k=1 (47) from the H1 1 Test, and Q h k=2 (47) and E h k=2 (47) from the H1 2 Test. Calulate all six quantities as speified in setion 3.7. Determine Q h k=2 (35) and E h k=2 (35) from the H2 2 Test and, if required as desribed in setion 3.6.3, determine Q h k=1 (35) and E h k=1 (35) from the H2 1 Test. Calulate the required 35 F quantities as speified in setion 3.9. Determine Q h k=2 (17) and E h k=2 (17) from the H3 2 Test and, if required as desribed in setion 3.6.3, determine Q h k=1 (17) and E h k=1 (17) from the H3 1 Test. Calulate the required 17 F quantities as speified in setion Steady-state spae heating apaity when operating at low ompressor apaity is greater than or equal to the building heating load at temperature T j, Q h k=1 (T j ) BL(T j ). where, X k=1 (T j ) = BL (T j ) / Q h k=1 (T j ), the heating mode low apaity load fator for temperature bin j, dimensionless. PLF j = 1 C Dh [1 X k=1 (T j )], the part load fator, dimensionless. δ'(t j ) = the low temperature utoff fator, dimensionless. If the optional H0C 1 Test desribed in setion is not onduted, set the heating mode yli degradation oeffiient, C D h, to the default value speified in setion If this optional test is onduted, set C D h to the lower of: a. The value alulated aording to setion 3.8.1; or b. The setion default value of

116 ANSI/ANSI/AHRI STANDARD 210/ Determine the low temperature ut-out fator using where T off and T on are defined in setion Use the alulations given in setion , and not the above, if: (a) The heat pump loks out low apaity operation at low outdoor temperatures and (b) T j is below this lokout threshold temperature Heat pump alternates between high (k=2) and low (k=1) ompressor apaity to satisfy the building heating load at a temperature T j, Q h k=1 (T j ) < BL (T j ) < Q h k=2 (T j ). Calulate using Equation Evaluate using where, X k=2 (T j ) = 1 X k=1 (T j ) the heating mode, high apaity load fator for temperature bin j, dimensionless. Determine the low temperature ut-out fator, δ'(t j ), using Equation Heat pump only operates at high (k=2) ompressor apaity at temperature T j and its apaity is greater than the building heating load, BL (T j ) < Q h k=2 (T j ). This setion applies to units that lok out low ompressor apaity operation at low outdoor temperatures. Calulate 106

117 ANSI/AHRI STANDARD 210/ using Equation Evaluate using where, X k=2 (T j ) = BL (T j )/ Q h k=2 (T j ). PLF j h k = 2 = 1 C k = 2) [ 1 X ( T )]. D ( j If the optional H1C 2 Test desribed in setion and Table 11 is not onduted, set ( k 2) speified in setion If this optional test is onduted, set ( k 2) a. the ( k 2) C h D = value alulated as per setion 3.8.1; or b. the setion default value for ( k 2) C h D =. C h D = to the lower of: ' Determine the low temperature ut-out fator, δ ( ), using Equation T j C h D = equal to the default value Heat pump must operate ontinuously at high (k=2) ompressor apaity at temperature T j, BL (T j ) Q h k=2 (T j ). Where 107

118 ANSI/ANSI/AHRI STANDARD 210/ Additional steps for alulating the HSPF of a heat pump having a variable-speed ompressor. Calulate HSPF using Equation Evaluate the spae heating apaity, Q h k=1 (T j ), and eletrial power onsumption, E h k=1 (T j ), of the heat pump when operating at minimum ompressor speed and outdoor temperature T j using where Q h k=1 (62) and E h k=1 (62) are determined from the H0 1 Test, Q h k=1 (47) and E h k=1 (47) are determined from the H1 1 Test, and all four quantities are alulated as speified in setion 3.7. Evaluate the spae heating apaity, Q h k=2 (T j ), and eletrial power onsumption, E h k=2 (T j ), of the heat pump when operating at maximum ompressor speed and outdoor temperature T j by solving Equations and , respetively, for k=2. Determine the Equation and quantities Q h k=2 (47) and E h k=2 (47) from the H1 2 Test and the alulations speified in setion 3.7. Determine Q h k=2 (35) and E h k=2 (35) from the H2 2 Test and the alulations speified in setion 3.9 or, if the H2 2 Test is not onduted, by onduting the alulations speified in setion Determine Q h k=2 (17) and E h k=2 (17) from the H3 2 Test and the alulations speified in setion Calulate the spae heating apaity, Q h k=v (T j ), and eletrial power onsumption, E h k=v (T j ), of the heat pump when operating at outdoor temperature T j and the intermediate ompressor speed used during the setion H2 V Test using where Q h k=v (35) and E h k=v (35) are determined from the H2 V Test and alulated as speified in setion 3.9. Approximate the slopes of the k=v intermediate speed heating apaity and eletrial power input urves, M Q and M E, as follows: M M Q E k Q h = E = (62) Q (47) k = 2 = 2 Q h (35) Qh (17) ( 1 N ) + N = 1 k = 1 k h Q Q (62) E (47) k = 2 = 2 E h (35) Eh (17) ( 1 N ) + N k = 1 k = 1 k h h E E where, Use Equations and , respetively, to alulate Q h k=1 (35) and E h k=1 (35). The alulation of Equation quantities 108

119 ANSI/AHRI STANDARD 210/ differs depending upon whether the heat pump would operate at minimum speed (setion ), operate at an intermediate speed (setion ), or operate at maximum speed (setion ) in responding to the building load Steady-state spae heating apaity when operating at minimum ompressor speed is greater than or equal to the building heating load at temperature T j, Q h k=1 (T j BL(T j ). Evaluate the Equation quantities as speified in setion Exept now use Equations and to evaluate Q h k=1 (T j ) and E h k=1 (T j ), respetively, and replae setion referenes to low apaity and setion with minimum speed and setion Also, the last sentene of setion does not apply Heat pump operates at an intermediate ompressor speed (k=i) in order to math the building heating load at a temperature T j, Q h k=1 (T j ) < BL (T j ) < Q h k=2 (T j ). Calulate using Equation while evaluating using, where, and δ(t j ) is evaluated using Equation while, Q h k=i (T j ) = BL (T j ), the spae heating apaity delivered by the unit in mathing the building load at temperature (T j ), Btu/h. The mathing ours with the heat pump operating at ompressor speed k=i. COP k=i (T j ) = the steady-state oeffiient of performane of the heat pump when operating at ompressor speed k=i and temperature T j, dimensionless. 109

120 ANSI/ANSI/AHRI STANDARD 210/ For eah temperature bin where the heat pump operates at an intermediate ompressor speed, determine COP k=i (T j ) using, COP k=i (T j ) = A + B T j + C T 2 j. For eah heat pump, determine the oeffiients A, B, and C by onduting the following alulations one: where, T 3 = the outdoor temperature at whih the heat pump, when operating at minimum ompressor speed, provides a spae heating apaity that is equal to the building load ( Q h k=1 (T 3 ) = BL(T 3 )), F. Determine T 3 by equating Equations and and solving for: outdoor temperature. T vh = the outdoor temperature at whih the heat pump, when operating at the intermediate ompressor speed used during the setion H2 V Test, provides a spae heating apaity that is equal to the building load ( Q h k=v (T vh ) = BL(T vh )), F. Determine T vh by equating Equations and and solving for outdoor temperature. T 4 = the outdoor temperature at whih the heat pump, when operating at maximum ompressor speed, provides a spae heating apaity that is equal to the building load ( Q h k=2 (T 4 ) = BL(T 4 )), F. Determine T 4 by equating Equations (k=2) and and solving for outdoor temperature. For multiple-split heat pumps (only), the following proedures supersede the above requirements for alulating k i COP = T ). For eah temperature bin where T 3 > T j > Tvh, h ( j 110

121 ANSI/AHRI STANDARD 210/ COP k= i h k= v k= 1 k= 1 COPh ( Tvh ) COPh ( T3 ) ( T j ) = COPh ( T3 ) + ( T j T3 ). T T For eah temperature bin where T vh T j > T 4, COP k= i h k= 2 k= v k= v COPh ( T4 ) COPh ( Tvh ) ( T j ) = COPh ( Tvh ) + ( T j Tvh ). T T vh 4 3 vh Heat pump must operate ontinuously at maximum (k=2) ompressor speed at temperature T j, BL (T j ) Q h k=2 (T j ). Evaluate the Equation quantities as speified in setion with the understanding that Q h k=2 (T j ) and E h k=2 (T j ) orrespond to maximum ompressor speed operation and are derived from the results of the speified setion tests Heat pumps having a heat omfort ontroller. Heat pumps having heat omfort ontrollers, when set to maintain a typial minimum air delivery temperature, will ause the heat pump ondenser to operate less beause of a greater ontribution from the resistive elements. With a onventional heat pump, resistive heating is only initiated if the heat pump ondenser annot meet the building load (i.e., is delayed until a seond stage all from the indoor thermostat). With a heat omfort ontroller, resistive heating an our even though the heat pump ondenser has adequate apaity to meet the building load (i.e., both on during a first stage all from the indoor thermostat). As a result, the outdoor temperature where the heat pump ompressor no longer yles (i.e., starts to run ontinuously), will be lower than if the heat pump did not have the heat omfort ontroller Heat pump having a heat omfort ontroller: additional steps for alulating the HSPF of a heat pump having a single-speed ompressor that was tested with a fixed-speed indoor fan installed, a onstant-air-volume-rate indoor fan installed, or with no indoor fan installed. Calulate the spae heating apaity and eletrial power of the heat pump without the heat omfort ontroller being ative as speified in setion (Equations and ) for eah outdoor bin temperature, T j, that is listed in Table 17. Denote these apaities and eletrial powers by using the subsript hp instead of h. Calulate the mass flow rate (expressed in pounds-mass of dry air per hour) and the speifi heat of the indoor air (expressed in Btu/lbm da F) from the results of the H1 Test using: where V s, V mx, v' n (or v n ), and W n are defined following Equation 3 1. For eah outdoor bin temperature listed in Table 17, alulate the nominal temperature of the air leaving the heat pump ondenser oil using, Evaluate e h (T j /N), RH (T j )/N, X (T j ), PLF j, and δ (T j ) as speified in setion For eah bin alulation, use the spae heating apaity and eletrial power from Case 1 or Case 2, whihever applies. Case 1. For outdoor bin temperatures where T o (T j ) is equal to or greater than T CC (the maximum supply temperature determined aording to setion 3.1.9), determine Q h (T j ) and E h (T j ) as speified in setion (i.e., Q h (T j ) = Q hp 111

122 ANSI/ANSI/AHRI STANDARD 210/ (T j ) and E hp (T j ) = E hp (T j )). Note: Even though T o (T j ) T, resistive heating may be required; evaluate Equation for all bins. Case 2. For outdoor bin temperatures where T o (T j ) > T, determine Q h(t j ) and E h(t j ) using, where, Note: Even though T o (T j ) < T, additional resistive heating may be required; evaluate Equation for all bins Heat pump having a heat omfort ontroller: additional steps for alulating the HSPF of a heat pump having a single-speed ompressor and a variable-speed, variable-air-volume-rate indoor fan. Calulate the spae heating apaity and eletrial power of the heat pump without the heat omfort ontroller being ative as speified in setion (Equations and ) for eah outdoor bin temperature, T j, that is listed in Table 17. Denote these apaities and eletrial powers by using the subsript hp instead of h. Calulate the mass flow rate (expressed in pounds-mass of dry air per hour) and the speifi heat of the indoor air (expressed in Btu/lbm da F) from the results of the H1 2 Test using: where V S, V mx, v' n (or v n ), and W n are defined following Equation 3 1. For eah outdoor bin temperature listed in Table 17, alulate the nominal temperature of the air leaving the heat pump ondenser oil using, Evaluate e h (T j )/N, RH(T j )/N, X(T j ), PLF j, and δ(t j ) as speified in setion with the exeption of replaing referenes to the H1C Test and setion with the H1C 1 Test and setion For eah bin alulation, use the spae heating apaity and eletrial power from Case 1 or Case 2, whihever applies. 112

123 ANSI/AHRI STANDARD 210/ Case 1. For outdoor bin temperatures where T o (T j ) is equal to or greater than T CC (the maximum supply temperature determined aording to setion 3.1.9), determine Q h (T j ) and E h (T j ) as speified in setion (i.e. Q h (T j ) = Q hp (T j ) and E h (T j ) = E hp (T j )). Note: Even though T o (T j ) T CC, resistive heating may be required; evaluate Equation for all bins. Case 2. For outdoor bin temperatures where T o (T j ) < T CC, determine Q h(t j ) and E h(t j ) using, Q h(t j ) = Q hp(t j ) + Q CC(T j ) E h(t j ) = E hp(t j ) + E CC(T j ) where, Q CC(T j ) = m da C p,da [T CC T o (T j )] Note: Even though T o (T j ) < T, additional resistive heating may be required; evaluate Equation for all bins Heat pumps having a heat omfort ontroller: additional steps for alulating the HSPF of a heat pump having a twoapaity ompressor. Calulate the spae heating apaity and eletrial power of the heat pump without the heat omfort ontroller being ative as speified in setion for both high and low apaity and at eah outdoor bin temperature, T j, that is listed in Table 17. Denote these apaities and eletrial powers by using the subsript hp instead of h. For the low apaity ase, alulate the mass flow rate (expressed in pounds-mass of dry air per hour) and the speifi heat of the indoor air (expressed in Btu/lbm da F) from the results of the H1 1 Test using: where V s, V mx, v' n (or v n ), and W n are defined following Equation 3 1. For eah outdoor bin temperature listed in Table 17, alulate the nominal temperature of the air leaving the heat pump ondenser oil when operating at low apaity using, Repeat the above alulations to determine the mass flow rate (m da k=2 ) and the speifi heat of the indoor air (C p, da k=2 ) when operating at high apaity by using the results of the H1 2 Test. For eah outdoor bin temperature listed in Table 17, alulate the nominal temperature of the air leaving the heat pump ondenser oil when operating at high apaity using, Evaluate e h (T j )/N, RH (T j )/N, X k=1 (T j ), and/or X k=2 (T j ), PLF j, and δ'(t j ) or δ"(t j ) as speified in setion , , or , whihever applies, for eah temperature bin. To evaluate these quantities, use the low-apaity spae 113

124 ANSI/ANSI/AHRI STANDARD 210/ heating apaity and the low-apaity eletrial power from Case 1 or Case 2, whihever applies; use the high-apaity spae heating apaity and the high-apaity eletrial power from Case 3 or Case 4, whihever applies. Case 1. For outdoor bin temperatures where T o k=1 (T j ) is equal to or greater than T CC (the maximum supply temperature determined aording to setion 3.1.9), determine Q h k=1 (T j ) and E h k=1 (T j ) as speified in setion (i.e., Q h k=1 (T j ) = Q hp k=1 (T j ) and E h k=1 (T j ) = E hp k=1 (T j ). Note: Even though T o k=1 (T j ) T CC, resistive heating may be required; evaluate RH (T j )/N for all bins. Case 2. For outdoor bin temperatures where T o k=1 (T j ) < T CC, determine Q h k=1 (T j ) and E h k=1 (T j ) using, Q h k=1 (T j ) = Q hp k=1 (T j ) + Q CC k=1 (T j ) E h k=1 (T j ) = E hp k=1 (T j ) + E CC k=1 (T j ) where, Note: Even though T o k=1 (T j ) T, additional resistive heating may be required; evaluate RH (T j )/N for all bins. Case 3. For outdoor bin temperatures where T k=2 o (T j ) is equal to or greater than T CC, determine Q h k=2 (T j ) and E h k=2 (T j ) as speified in setion (i.e., Q h k=2 (T j ) = Q hp k=2 (T j ) and E h k=2 (T j ) = E hp k=2 (T j )). Note: Even though T k=2 o (T j ) < T CC, resistive heating may be required; evaluate RH (T j )/N for all bins. Case 4. For outdoor bin temperatures where T o k=2 (T j ) < T CC, determine Q h k=2 (T j ) and E h k=2 (T j ) using, where, Note: Even though T o k=2 (T j ) < T, additional resistive heating may be required; evaluate RH (T j )/N for all bins. 114

125 ANSI/AHRI STANDARD 210/ Heat pumps having a heat omfort ontroller: additional steps for alulating the HSPF of a heat pump having a variable-speed ompressor. [Reserved] 4. Calulations of the Atual and Representative Regional Annual Performane Fators for Heat Pumps Calulation of atual regional annual performane fators (APF A ) for a partiular loation and for eah standardized design heating requirement. where, CLH A = the atual ooling hours for a partiular loation as determined using the map given in Figure 3, hr. Q k (95) = the spae ooling apaity of the unit as determined from the A or A 2 Test, whihever applies, Btu/h. HLH A = the atual heating hours for a partiular loation as determined using the map given in Figure 2, hr. DHR = the design heating requirement used in determining the HSPF; refer to setion 4.2 and Definition 1.22, Btu/h. C = defined in setion 4.2 following Equation 4.2 2, dimensionless. SEER = the seasonal energy effiieny ratio alulated as speified in setion 4.1, Btu/W h. HSPF = the heating seasonal performane fator alulated as speified in setion 4.2 for the generalized limati region that inludes the partiular loation of interest (see Figure 2), Btu/W h. The HSPF should orrespond to the atual design heating requirement (DHR), if known. If it does not, it may orrespond to one of the standardized design heating requirements referened in setion Calulation of representative regional annual performane fators (APF R ) for eah generalized limati region and for eah standardized design heating requirement. where, CLH R = the representative ooling hours for eah generalized limati region, Table 19, hr. HLH R = the representative heating hours for eah generalized limati region, Table 19, hr. HSPF = the heating seasonal performane fator alulated as speified in setion 4.2 for the eah generalized limati region and for eah standardized design heating requirement within eah region, Btu/W h. The SEER, Q k (95), DHR, and C are the same quantities as defined in setion Figure 2 shows the generalized limati regions. Table 18 lists standardized design heating requirements. 115

126 ANSI/ANSI/AHRI STANDARD 210/ Table 19. Representative Cooling and Heating Load Hours for Eah Generalized Climati Region Region CLH R HLH R I II... III... IV... V... VI Rounding of SEER, HSPF, and APF for reporting purposes. After alulating SEER aording to setion 4.1, round it off as speified in subpart B (m)(3)(i) of Title 10 of the Code of Federal Regulations. Round setion 4.2 HSPF values and setion 4.3 APF values as per (m) (3) (ii) and (iii) of Title 10 of the Code of Federal Regulations. 116

127 ANSI/AHRI STANDARD 210/ For questions or omments regarding e-cfr editorial ontent, features, or design, For questions onerning e-cfr programming and delivery issues, Last updated: July 27,

2010 Standard for Performance Rating of Variable Refrigerant Flow (VRF) Multi-Split Air-Conditioning and Heat Pump Equipment

2010 Standard for Performance Rating of Variable Refrigerant Flow (VRF) Multi-Split Air-Conditioning and Heat Pump Equipment ANSI/AHRI Standard 1230 with Addendum 2 2010 Standard for Performance Rating of Variable Refrigerant Flow (VRF) Multi-Split Air-Conditioning and Heat Pump Equipment Approved by ANSI on 2 August 2010 ANSI/AHRI

More information

Energy Saving Opportunities through Heat Recovery from Cement Processing Kilns: A Case Study

Energy Saving Opportunities through Heat Recovery from Cement Processing Kilns: A Case Study Energy Saving Opportunities through Heat Reovery from Cement Proessing Kilns: A Case Study I. I. AL-HINTI a, A. AL-GHANDOOR b, A. AL-NAJI, M. ABU-KHASHABEH, M. JOUDEH, M. AL-HATTAB a Department of Mehanial

More information

Energy Recovery Ventilation Equipment

Energy Recovery Ventilation Equipment ANSI/AHRI Standard 1060 (I-P) 2014 Standard for Performance Rating of Airto-Air Exchangers for Energy Recovery Ventilation Equipment Approved by ANSI on May 15, 2015 IMPORTANT SAFETY DISCLAIMER AHRI does

More information

SINGLE PACKAGED VERTICAL AIR-CONDITIONERS AND HEAT PUMPS CERTIFICATION PROGRAM

SINGLE PACKAGED VERTICAL AIR-CONDITIONERS AND HEAT PUMPS CERTIFICATION PROGRAM SINGLE PACKAGED VERTICAL AIR-CONDITIONERS AND HEAT PUMPS CERTIFICATION PROGRAM AHRI SPVA AND SPVH OM JANUARY 2018 2111 Wilson Blvd, Suite 500 Arlington, Virginia 22201 (703) 524-8800 Sponsored and administered

More information

Cabinet Features Heavy-gauge, galvanizedsteel. powder-paint finish Full perimeter rail Sloped drain pan Easy to service

Cabinet Features Heavy-gauge, galvanizedsteel. powder-paint finish Full perimeter rail Sloped drain pan Easy to service DG ommercial 7½- TO ½-TON THREE-PHASE PAKAGED GAS/ ELETRI UP TO. EER / 80% AUE ooling apacity: 88,000,000 BTU/h Heating apacity (Output): 68,000 BTU/h ontents Nomenclature... Product Specifications...

More information

Thermal Analysis of Open-Cycle Regenerator Gas-Turbine Power-Plant

Thermal Analysis of Open-Cycle Regenerator Gas-Turbine Power-Plant Thermal Analysis of Open-Cyle Regenerator Gas-Turbine Power-Plant M. M. Rahman, Thamir K. Ibrahim, M. Y. Taib, M. M. Noor, K. Kadirgama and Rosli A. Bakar Abstrat Regenerative gas turbine engine yle is

More information

Calculating the Efficiency of Energy Recovery Ventilation and its Effect on Efficiency and Sizing of Building HVAC Systems

Calculating the Efficiency of Energy Recovery Ventilation and its Effect on Efficiency and Sizing of Building HVAC Systems AHRI Guideline V (I-P) 20 Guideline for Calculating the Efficiency of Energy Recovery Ventilation and its Effect on Efficiency and Sizing of Building HVAC Systems IMPORTANT SAFETY DISCLAIMER AHRI does

More information

Camber Variability in Prestressed Concrete Bridge Beams

Camber Variability in Prestressed Concrete Bridge Beams CONCRETE BRIDGE TECHNOLOGY Camber Variability in Prestressed Conrete Bridge Beams by Dr. Maher Tadros, econstrut Beams ast with extra amber in storage yard at Conrete Tehnology Corporation; amber shown

More information

Comparison Study of Connector and Tubing Blow-Off Line

Comparison Study of Connector and Tubing Blow-Off Line PROCEEDINGS Comparison Study of Connetor and Tubing Blow-Off Line Pressures Jerry D. Leaf, Charles Dyson, Robert Emerson UCLA Medial Center, Department of Surgery, Division of Thorai Surgery Abstrat The

More information

Composite Steel Floor Deck-Slabs

Composite Steel Floor Deck-Slabs AMERICAN NATIONAL STANDARDS / STEEL DECK C - 2017 Standard for Composite Steel Floor Dek-Slabs opyright 2017 steel dek institute 1. General AMERICAN NATIONAL STANDARDS / STEEL DECK 1.1 Sope: A. This Standard

More information

BBR VT CONA CMI BT. Internal Post-tensioning System with 02 to 61 Strands. European Technical Approval ETA 09/0286

BBR VT CONA CMI BT. Internal Post-tensioning System with 02 to 61 Strands. European Technical Approval ETA 09/0286 BBR VT with 02 to 61 Strands European Tehnial Approval ETA 09/0286 0432 BBR VT with 02 to 61 Strands BBR VT International Ltd Bahnstrasse 23, 8603 Shwerzenbah (Switzerland) www.bbrnetwork.om S P E C I

More information

Keywords: Greenhouse; Thermal performance; Water pipes heating; Infrared radiation; Energy balance; Heating efficiency

Keywords: Greenhouse; Thermal performance; Water pipes heating; Infrared radiation; Energy balance; Heating efficiency International Symposium Greensys 7 "High Tehnology for Greenhouse system Management" Naples Italy, 4-6 Otober 7 Investigation of the Potential of Infrared-radiation (IR) to Redue Energy Consumption in

More information

VARIABLE REFRIGERANT FLOW MULTI-SPLIT AIR-CONDITIONERS AND HEAT PUMPS CERTIFICATION PROGRAM

VARIABLE REFRIGERANT FLOW MULTI-SPLIT AIR-CONDITIONERS AND HEAT PUMPS CERTIFICATION PROGRAM VARIABLE REFRIGERANT FLOW MULTI-SPLIT AIR-CONDITIONERS AND HEAT PUMPS CERTIFICATION PROGRAM VRF OM JANUARY 2018 2111 Wilson Boulevard, Suite 500 Arlington, Virginia 22201 (703) 524-8800 Sponsored and administered

More information

European Regulations For Multilayer Food Contact Materials. Dr. Hermann Onusseit Henkel KGaA Düsseldorf, Germany ABSTRACT

European Regulations For Multilayer Food Contact Materials. Dr. Hermann Onusseit Henkel KGaA Düsseldorf, Germany ABSTRACT European Regulations For Multilayer Food Contat Materials Dr. Hermann Onusseit Henkel KGaA Düsseldorf, Germany ABSTRACT Artiles and failities whih ome into ontat with food are subjet to speial demands.

More information

COCCUS Farm 75 kw Small Biogas Plant for Livestock Farmers

COCCUS Farm 75 kw Small Biogas Plant for Livestock Farmers COCCUS Farm 75 kw Small Biogas Plant for Livestok Farmers Plant tehnology Fig. similar COCCUS Farm 75 kw The COCCUS Farm 75 kw plant allows even small farms to reate a seondary soure of inome. COCCUS Farm

More information

ENGINEERED DESIGN OF SIP PANELS USING NTA LISTING REPORT DATA

ENGINEERED DESIGN OF SIP PANELS USING NTA LISTING REPORT DATA ENGINEERED DESIGN OF SI ANELS USING NTA LISTING REORT DATA 1. SCOE 1.1. GENERAL This doument applies to strutural insulated panels (SIs), whih shall be deined as a strutural aing material with a oam ore.

More information

Thermodynamic Analysis of Combined Cycle Power Plant

Thermodynamic Analysis of Combined Cycle Power Plant Thermodynami Analysis of Combined Cyle Power Plant A.K.Tiwari 1, Mohd Islam 2, M.N.Khan 3 1 Greater.Noida.Institute of Tehnology, Greater Noida, India. 2 Jamia Millia Islamia,New Delhi, India. 3 Krishna

More information

Suspended ceiling with visible T-sections

Suspended ceiling with visible T-sections Suspended eiling with visible T-setions a E E E max. 300 mm a m Hanger spaing 1 Hanging system: Rihter System 11.2 D 2 E C 26 C Main setion spaing E A Suspended eiling with visible T-setions Produts Table

More information

Computer applications for selecting operating parameters in a stationary grain crop thresher

Computer applications for selecting operating parameters in a stationary grain crop thresher Journal of Agriultural Tehnology 011 Vol. 7(1): 39-56 Journal of Available Agriultural online Tehnology http://www.ijat-rmutto.om 011 Vol. 7(1): 39-56 ISSN 1686-9141 Computer appliations for seleting operating

More information

New Case Hardening Software SimCarb QuenchTemp for the Simulation of Hardness and Microstructure from Carburization Profiles

New Case Hardening Software SimCarb QuenchTemp for the Simulation of Hardness and Microstructure from Carburization Profiles New ase Hardening Software Simarb QuenhTemp for the Simulation of Hardness and Mirostruture from arburization Profiles M. Kaffenberger 1,a, J. Gegner 1,b 1 University of Siegen, Institute of Material Siene,

More information

UNITARY SMALL AIR-CONDITIONERS AND AIR-SOURCE HEAT PUMPS (INCLUDES MIXED-MATCH COILS) (RATED BELOW 65,000 BTU/H) CERTIFICATION PROGRAM

UNITARY SMALL AIR-CONDITIONERS AND AIR-SOURCE HEAT PUMPS (INCLUDES MIXED-MATCH COILS) (RATED BELOW 65,000 BTU/H) CERTIFICATION PROGRAM UNITARY SMALL AIR-CONDITIONERS AND AIR-SOURCE HEAT PUMPS (INCLUDES MIXED-MATCH COILS) (RATED BELOW 65,000 BTU/H) CERTIFICATION PROGRAM USE AHRI OM JANUARY 2018 2111 Wilson Blvd, Suite 500 Arlington, Virginia

More information

Minimization of water and chemical usage in the cleaning in place process of a milk pasteurization plant

Minimization of water and chemical usage in the cleaning in place process of a milk pasteurization plant Songklanakarin J. Si. Tehnol. 33 (4), 431-440, Jul. - Aug. 2011 http://www.sjst.psu.a.th Original Artile Minimization of water and hemial usage in the leaning in plae proess of a milk pasteurization plant

More information

Prediction of Temperature and Aging Effects on the Properties of Concrete

Prediction of Temperature and Aging Effects on the Properties of Concrete Predition of Temperature and Aging Effets on the Properties of Conrete Jin-Keun Kim 1* and Inyeop Chu 1 1 KAIST, Republi of Korea * E-mail: kimjinkeun@kaist.a.kr ABSTRACT For the sustainable onrete strutures,

More information

Steel. Members. in medium to. composite. provisions for. the available. b) strength of. design,

Steel. Members. in medium to. composite. provisions for. the available. b) strength of. design, Chapter 13 Steel Conrete Composite Strutural Members 13.1 General Provisions for Steel Conrete Composite Strutural Members This setion states the sope of the speifiation, summarizess referened speifiations,

More information

HEAT PUMP POOL HEATERS CERTIFICATION PROGRAM

HEAT PUMP POOL HEATERS CERTIFICATION PROGRAM HEAT PUMP POOL HEATERS CERTIFICATION PROGRAM AHRI HPPH OM JANUARY 2017 2111 Wilson Blvd, Suite 500 Arlington, Virginia 22201 (703) 524-8800 Sponsored and administered by: PREFACE The following manual outlines

More information

Engineering Properties of Manganese-Treated Asphalt Mixtures

Engineering Properties of Manganese-Treated Asphalt Mixtures 56 Transportation Researh Reord 134 Engineering Properties of Manganese-Treated Asphalt Mixtures THOMAS W. KENNEDY and JON EPPS ABSTRACT An experimental program as onduted to evaluate the engineering properties

More information

BUILDINGS & PHOTOVOLTAICS GRID-CONNECTED PV-SYSTEMS

BUILDINGS & PHOTOVOLTAICS GRID-CONNECTED PV-SYSTEMS Bekaert ECD Solar Systems LLC R BUILDINGS & PHOTOVOLTAICS GRID-CONNECTED PV-SYSTEMS Unique Photovoltai Tehnology based on: Shingles Metal Roofing Framed Power Modules UNI-SOLAR ROOFING SYSTEMS The leader

More information

WAER QUALITY CAPTURE VOLUME FOR STORMWATER BMP and LID DESIGNS

WAER QUALITY CAPTURE VOLUME FOR STORMWATER BMP and LID DESIGNS Guo, James C. Y. Urbonas, B. and MaKenzie K. (2012) Water Quality Capture Volume for LID and BMP Designs, HEENG- 1539, aepted for publiation on ASCE J of Hydrologi Engineering, Ot, 2012 WAER QUALITY CAPTURE

More information

Post-Tensioned Two-Way Slab

Post-Tensioned Two-Way Slab The Medial Oie Building Malvern, PA 13 Post-Tensioned Two-Way Slab Introdution The Filigree beam system reates a thin lightweight loor system that leaves plenty o open plenum spae or mehanial and eletrial

More information

Strength of Glass from Hertzian Line Contact

Strength of Glass from Hertzian Line Contact Strength of Glass from Hertzian Line Contat Wenrui Cai, Brian Cuerden, Robert E. Parks, James H. Burge College of Optial Sienes, University of Arizona, Tuson, AZ USA 85721 Phone: 52-626-486, 52-621-8182

More information

Accepted Manuscript. Factors affecting moment redistribution at ultimate in continuous beams prestressed with external CFRP tendons

Accepted Manuscript. Factors affecting moment redistribution at ultimate in continuous beams prestressed with external CFRP tendons Aepted Manusript Fators affeting moment redistribution at ultimate in ontinuous beams prestressed with external CFRP tendons Tiejiong Lou, Sergio M.R. Lopes, Adelino V. Lopes PII: S1359-8368(14)00205-4

More information

GROUND WATER/SURFACE WATER INTERACTIONS AWRA SUMMER SPECULLTP CONF~NCR CZ-I PDG- ANALYSIS OF INFILTRATED STREAM WATER TO A PUMPING WELL

GROUND WATER/SURFACE WATER INTERACTIONS AWRA SUMMER SPECULLTP CONF~NCR CZ-I PDG- ANALYSIS OF INFILTRATED STREAM WATER TO A PUMPING WELL JULY 1-3 GROUND WATER/SURFACE WATER NTERACTONS AWRA SUMMER SPECULLTP CONF~NCR 22 32 CZ- PDG- ANALYSS OF NFLTRATED STREAM WATER TO A PUMPNG WELL Xunhong Chen' and Xi Chen' ABSTRACT: Pumping of groundwater

More information

EXPERIMENTAL INVESTIGATION OF ECCENTRIC REINFORCED CONCRETE BEAM-COLUMN-SLAB CONNECTIONS UNDER EARTHQUAKE LOADING

EXPERIMENTAL INVESTIGATION OF ECCENTRIC REINFORCED CONCRETE BEAM-COLUMN-SLAB CONNECTIONS UNDER EARTHQUAKE LOADING 13 th World Conferene on Earthquake Engineering Vanouver, B.C., Canada August 1-6, 24 Paper No. 215 EXPERIMENTAL INVESTIGATION OF ECCENTRIC REINFORCED CONCRETE BEAM-COLUMN-SLAB CONNECTIONS UNDER EARTHQUAKE

More information

Technical Data. Neutral 20. Single Pane Tinted Double Pane Double tinted Neutral 1/4" Neutral Dual 1/4" Neutral Dual 1/4" Neutral.

Technical Data. Neutral 20. Single Pane Tinted Double Pane Double tinted Neutral 1/4 Neutral Dual 1/4 Neutral Dual 1/4 Neutral. 20 (RE20NEARL) Redue air onditioning osts. Stay ooler by reduing exessive heat in warmer months. Redues glare and eye disomfort. Extend the life and vibrany in the fabri of furniture and arpets. Redues

More information

Economic Assessment of Intensive Culture

Economic Assessment of Intensive Culture Reprodued from JOURNAL OF FORESTRY, Vol. 76, No. 11, November 1978, by the FOREST SERVICE, U.S. Department of Agriulture, for offiial use. About This File:,. lhis file was reated by sanning the printed

More information

EXERGY BASED METHODS FOR ECONOMIC AND ENVIRONMENTAL ANALYSIS APPLIED TO A 320 MW COMBINED CYCLE POWER PLANT

EXERGY BASED METHODS FOR ECONOMIC AND ENVIRONMENTAL ANALYSIS APPLIED TO A 320 MW COMBINED CYCLE POWER PLANT 12th Joint European Thermodynamis Conferene Bresia, July 1-5, 2013 EXERGY BASED METHODS FOR ECONOMIC AND ENVIRONMENTAL ANALYSIS APPLIED TO A 320 MW COMBINED CYCLE POWER PLANT Matteo Roo*, Claudia Toro

More information

SEISMIC RETROFIT USING CONTINUOUS FIBER SHEETS

SEISMIC RETROFIT USING CONTINUOUS FIBER SHEETS SEISMIC RETROFIT USING CONTINUOUS FIER SHEETS Yasuhiro MATSUZAKI 1, Katsuhiko NAKANO, Shigeru FUJII 3 And Hiroshi FUKUYAMA 4 SUMMARY The researh on seismi retrofit of RC members using ontinuous fiber sheets

More information

HEAT EXCHANGERS HEAT EXCHANGERS: TYPES

HEAT EXCHANGERS HEAT EXCHANGERS: TYPES HEAT EXCHANGERS Heat exhangers: types... 1 Plate heat exhangers... 4 Shell-and-tube heat exhangers... 5 Boilers... 6 Charateristis... 8 Heat exhanger analysis... 10 Overall heat-transfer oeffiient... 10

More information

KE double wall transport anchors

KE double wall transport anchors for better solutions... KE double wall transport anhors The safe transport anhor for double walls KE Ttransport anhors - Transport double walls seurely www.h-bau.de Contat Oslo Helsinki Mosow London Warsaw

More information

Studies and research applications involving

Studies and research applications involving VOL. 8():99-9 99 Amerian Soietv of Agriultural Engineers 000-^^ / 0 / ^Rm-OO^o DIAGNOSTI HARDWARE/SOFTWARE SYSTEM FOR ENVIRONMENT ONTROLLERS K. hao, R. S. Gates, H.-. hi ABSTRAT. A system onsisting of

More information

IMPROVEMENTS IN DOMESTIC WATER SERVICES IN KELANTAN: ARE PEOPLE WILLING TO PAY?

IMPROVEMENTS IN DOMESTIC WATER SERVICES IN KELANTAN: ARE PEOPLE WILLING TO PAY? Journal of Sustainability Siene and Management Volume 8 Number 2, Deember 2013: 61-70 ISSN: 1823-8556 Penerbit UMT IMPROVEMENTS IN DOMESTIC WATER SERVICES IN KELANTAN: ARE PEOPLE WILLING TO PAY? MAHIRAH

More information

Tapper Concrete Scew Anchor Type 410 & 304 Stainless Steel

Tapper Concrete Scew Anchor Type 410 & 304 Stainless Steel Conrete Sew Type 4 & 304 PRODUCT DESCRIPTION The fastening system is a family of srew anhors for light to meium uty appliations in onrete, masonry blok an brik base materials. The is fast an easy to install

More information

THE ENERGY DISSIPATION EFFECTS OF REDUNDANT MEMBERS IN SILOS UNDER EARTHQUAKES

THE ENERGY DISSIPATION EFFECTS OF REDUNDANT MEMBERS IN SILOS UNDER EARTHQUAKES 269 THE ENEGY DISSIPATION EFFECTS OF EDUNDANT MEMBES IN SILOS UNDE EATHQUAKES Li Zhiming 1 and Geng Shujiang 1 SUMMAY An analytial study is made the response to strong base motion reinfored onrete silo

More information

A New Tri-Generation System: Thermodynamical Analysis of a Micro Compressed Air Energy Storage

A New Tri-Generation System: Thermodynamical Analysis of a Micro Compressed Air Energy Storage Journal of nergy and Power ngineering 10 (2016) 697-707 doi: 10.17265/1934-8975/2016.11.007 D DAVID PUBLISHING A New Tri-Generation System: Thermodynamial Analysis of a Miro Compressed Air nergy Storage

More information

Proceedings of the 2012 Winter Simulation Conference C. Laroque, J. Himmelspach, R. Pasupathy, O. Rose, and A.M. Uhrmacher, eds

Proceedings of the 2012 Winter Simulation Conference C. Laroque, J. Himmelspach, R. Pasupathy, O. Rose, and A.M. Uhrmacher, eds Proeedings of the 2012 Winter Simulation Conferene C. Laroque, J. Himmelspah, R. Pasupathy, O. Rose, and A.M. Uhrmaher, eds INDUSTRIAL IMPLEMENTATION OF A DYNAMIC SAMPLING ALGORITHM IN SEMICONDUCTOR MANUFACTURING:

More information

An Analysis of Baffles Designs for Limiting Fluid Slosh in Partly Filled Tank Trucks

An Analysis of Baffles Designs for Limiting Fluid Slosh in Partly Filled Tank Trucks The Open Transportation Journal, 21, 4, 23-32 23 Open Aess An Analysis of Baffles Designs for Limiting Fluid Slosh in Partly Filled Tank Truks T. Kandasamy, S. Rakheja * and A.K.W. Ahmed CONCAVE Researh

More information

A COMPARATIVE ANALYSIS OF TWO COMPETING MID-SIZE OXY-FUEL COMBUSTION CYCLES T U

A COMPARATIVE ANALYSIS OF TWO COMPETING MID-SIZE OXY-FUEL COMBUSTION CYCLES T U Proeedings of ASME Turbo Expo 2012: Power for Land, Sea and Air GT2012 June 11-15, 2012, Copenhagen, Denmark GT2012-69676 A COMPARATIVE ANALYSIS OF TWO COMPETING MID-SIZE OXY-FUEL COMBUSTION CYCLES Egill

More information

CIS Guidance Document on WFD Article 4(7) SUMMARY OF COMMENTS ON DRAFT 1

CIS Guidance Document on WFD Article 4(7) SUMMARY OF COMMENTS ON DRAFT 1 General Comments Line Nr. Comment/hange request Justifiation of the omment/hange request MS Comment by drafters General Further integration of groundwater issues is needed throughout the More overage lf

More information

The Impact of Climate Variability and Change on Economic Growth and Poverty in Zambia

The Impact of Climate Variability and Change on Economic Growth and Poverty in Zambia The Impat of Climate Variability and Change on Eonomi Growth and Poverty in Zambia James Thurlow, Tingju Zhu and Xinshen Diao 1 International Food Poliy Researh Institute Deember 2008 1 We are grateful

More information

USING REAL-TIME INFORMATION IN PRODUCTION PLANNING AND OPERATIONAL CONTROL

USING REAL-TIME INFORMATION IN PRODUCTION PLANNING AND OPERATIONAL CONTROL 9 th International Conferene on Prodution Researh USING REAL-TIME INFORMATION IN PRODUCTION PLANNING AND OPERATIONAL CONTROL Ronald G. Askin, Detlef Pabst, Mihael Pew, Young Jun Son 2 Department of Industrial

More information

Comparison of Fuzzy Analytic Hierarchy Process and Analytic Hierarchy Process Based Decision Support for a Lean Performance Measurement System

Comparison of Fuzzy Analytic Hierarchy Process and Analytic Hierarchy Process Based Decision Support for a Lean Performance Measurement System Journal of Oean, Mehanial and erospae -Siene and Engineering-, Vol. 9 Marh 0, 06 Comparison of Fuzzy nalyti Hierarhy Proess and nalyti Hierarhy Proess ased Deision Support for a Lean Performane Measurement

More information

AUTOSAW SYSTEM FOR SAWING SIMULATION

AUTOSAW SYSTEM FOR SAWING SIMULATION AUTOSAW SYSTEM FOR SAWING SIMULATION C. L. TODOROKI Ministry of Forestry, Forest Researh Institute, Private Bag, Rotorua, New Zealand (Reeived for publiation November 99; revision 9 Deember 99) ABSTRACT

More information

LIGHTWEIGHT CONCRETE MATERIAL PROPERTIES FOR STRUCTURAL DESIGN. Henry G. Russell, Henry G. Russell, Inc., Glenview, IL

LIGHTWEIGHT CONCRETE MATERIAL PROPERTIES FOR STRUCTURAL DESIGN. Henry G. Russell, Henry G. Russell, Inc., Glenview, IL LIGHTWEIGHT CONCRETE MATERIAL PROPERTIES FOR STRUCTURAL DESIGN Henry G. Russell, Henry G. Russell, In., Glenview, IL ABSTRACT This paper ontains a ompilation and synthesis of researh relating to lightweight

More information

Effects of Electrode Composition, Flux Basicity, and Slag Depth on Grain-Boundary Cracking in Electroslag Weld Metals

Effects of Electrode Composition, Flux Basicity, and Slag Depth on Grain-Boundary Cracking in Electroslag Weld Metals Effets of omposition, Basiity, and Slag Depth on GrainBoundary raking in Eletroslag Weld Metals An aidi flux, a high slag depth, and highsilion eletrodes are found to help eliminate grainboundary raking

More information

Study of the simulation model of a displacementsensitive shock absorber of a vehicle by considering the fluid force

Study of the simulation model of a displacementsensitive shock absorber of a vehicle by considering the fluid force Study of the simulation model of a displaementsensitive shok absorber of a vehile by onsidering the fluid fore Choon-Tae Lee1 and Byung-Young Moon2* 1Department of Mehanial and Intelligent Systems Engineering,

More information

Experimental Study of a New Type Buckling-Restrained Brace. Abstract

Experimental Study of a New Type Buckling-Restrained Brace. Abstract Experimental Study of a New Type Bukling-Restrained Brae S. G. CHENG, X.X. KONG AND K.H. LUO Institute of Earthquake Engineering, China Aademy of Building Researh Abstrat The steel ore and unbonding agent

More information

Optimized Execution of Business Processes on Crowdsourcing Platforms

Optimized Execution of Business Processes on Crowdsourcing Platforms 8th International Conferene Conferene on Collaborative Computing: Networking, Appliations and Worksharing, Collaborateom 212 Pittsburgh, PA, United States, Otober 14-17, 212 Optimized Exeution of Business

More information

Unitary Air Conditioner Field Performance

Unitary Air Conditioner Field Performance Purdue University Purdue e-pubs International Refrigeration and Air Conditioning Conference School of Mechanical Engineering 2004 Unitary Air Conditioner Field Performance Todd M. Rossi Field Diagnostic

More information

SULPHUR BEHAVIOUR UNDER CHANGING PARTIAL PRESSURE OF CO IN REFINING OF FeCr ALLOY

SULPHUR BEHAVIOUR UNDER CHANGING PARTIAL PRESSURE OF CO IN REFINING OF FeCr ALLOY SULPHUR BEHAVIOUR UNDER CHANGING PARTIAL PRESSURE OF CO IN REFINING OF FeCr ALLOY Xoiwei Pan and Rauf Horman Eri Shool of Proess and Materials Engineering University of the Witwatersrand, Johannesburg

More information

Supplementary Materials for

Supplementary Materials for advanes.sienemag.org/gi/ontent/full/3/4/e1602629/dc1 Supplementary Materials for Single-layer nanosheets with exeptionally high and anisotropi hydroxyl ion ondutivity Pengzhan Sun, Renzhi Ma, Xueyin Bai,

More information

Architecture of an ERP System Supporting Project-Oriented Management

Architecture of an ERP System Supporting Project-Oriented Management Arhiteture of an ERP System Supporting Projet-Oriented Management Willy Piard and Grzegorz Wojiehowski Department of Information Tehnology The Poznań University of Eonomis ul. Mansfelda 4 60-854 Poznań,

More information

Carbon Dioxide Capture & Conversion (CO 2 CC) Program A Membership Program offered by The Catalyst Group Resources (TCGR)

Carbon Dioxide Capture & Conversion (CO 2 CC) Program A Membership Program offered by The Catalyst Group Resources (TCGR) Carbon Dioxide Capture & Conversion (CO 2 CC) Program A Membership Program offered by The Catalyst Group Resoures (TCGR) 2018 P.O. Box 680 Spring House, PA 19477 USA Tel: (215) 628-4447 Fax: (215) 628-2267

More information

Example 24.3 Flexural Strength of Prestressed Member Using Approximate Value for f ps

Example 24.3 Flexural Strength of Prestressed Member Using Approximate Value for f ps Example 24.3 Flexural Strength of Prestressed Member Using Approximate Value for f ps Calulate the nominal moment strength of the prestressed member shown. f = 5000 psi f pu = 270,000 psi (low-relaxation

More information

20 questions on genetically modified foods

20 questions on genetically modified foods Page 1 of 6 Searh All WHO This site only Home About WHO Countries Health topis Publiations Data and statistis Programmes and projets Food Safety Zoonoses Mirobiologial risks Chemial risks Biotehnology

More information

GGDC PRODUCTIVITY LEVEL DATABASE:

GGDC PRODUCTIVITY LEVEL DATABASE: GGDC PRODUCTIVITY EVE DATABASE: INTERNATIONA COMPARISONS OF OUTPUT, INPUTS AND PRODUCTIVITY AT THE INDUSTRY EVE Robert Inklaar and Marel P. Timmer* Groningen Growth and Development Centre University of

More information

in Shake Flask Experiments

in Shake Flask Experiments APPLIED AND ENVIRONMENTAL MICROBIOLOGY, Jan. 1991, p. 138-145 Vol. 57, No. 1 99-224/91/1138-8$2./ Copyright 1991, Amerian Soiety for Mirobiology Temperature Effets on Baterial Leahing of Sulfide Minerals

More information

2011 Standard for Performance Rating Of Water-Chilling and Heat Pump Water-Heating Packages Using the Vapor Compression Cycle

2011 Standard for Performance Rating Of Water-Chilling and Heat Pump Water-Heating Packages Using the Vapor Compression Cycle ANSI/AHRI Standard 550/590 (I-P) with Addendum 3 2011 Standard for Performance Rating Of Water-Chilling and Heat Pump Water-Heating Packages Using the Vapor Compression Cycle Approved by ANSI on June 18,

More information

Heating, Ventilation & Air Conditioning Systems ( Member Information Page )

Heating, Ventilation & Air Conditioning Systems ( Member Information Page ) 2017 Commercial Program Heating, Ventilation & Air Conditioning Systems ( Member Information Page ) WrightHennepin Cooperative Electric Assn., P.O. Box 330, Rockford, MN 55373 Ph: 7634773000 Business Member

More information

AN ADVERTISING OLIGOPOLY

AN ADVERTISING OLIGOPOLY The USV Annals of Eonomis and Publi Administration Volume 3, Issue (8), 03 AN ADVERTISING OLIGOPOLY Ph.D. Student Alina Irina GHIRVU Faulty of Eonomial Sienes and Business Administration Babeş Bolyai University,

More information

An Evaluation of Environmental Impacts of Different Truck Sizes in Last Mile Distribution in the city of São Paulo, Brazil

An Evaluation of Environmental Impacts of Different Truck Sizes in Last Mile Distribution in the city of São Paulo, Brazil An Evaluation of Environmental Impats of Different Truk Sizes in Last Mile Distribution in the ity of São Paulo, Brazil Nathalia C. Zambuzi 1, Claudio B. Cunha 1, Edgar Blano 2, Hugo Yoshizaki 1, Carla

More information

WSF Working Paper Series

WSF Working Paper Series WSF Working Paper Series GlobLabWS #1/2016 November 2016 Firm Size Distribution and Employment Flutuations: Theory and Evidene H. Görg, P. Henze, V. Jienwatharamongkhol, D. Kopasker, H Molana, C. Montagna,

More information

PASSIVE SOLAR ENERGY AS A FUEL

PASSIVE SOLAR ENERGY AS A FUEL PASSIV SOLAR NRGY AS A FUL 199-21 A study of the urrent and future use of passive solar energy in buildings in the uropean Community. RPORT ON BACKGROUND MATRIAL AND RSARCH The Commission of the uropean

More information

The GAINS model. 1 Introduction

The GAINS model. 1 Introduction The GAINS model Introdution The Greenhouse gas - Air pollution Interations and Synergies (GAINS) model (http://gains.iiasa.a.at/) has been developed at the International Institute for Applied Systems Analysis

More information

Welfare impacts of alternative biofuel and energy policies

Welfare impacts of alternative biofuel and energy policies Eonomis Working Papers (2002 2016) Eonomis 6-9-2010 Welfare impats of alternative biofuel and energy poliies Jingbo Cui Iowa State University, jbui2013@gmail.om Harvey E. Lapan Iowa State University, hlapan@iastate.edu

More information

Conducted in Bangkok-Thonburi, Thailand, in 1969*

Conducted in Bangkok-Thonburi, Thailand, in 1969* 27 OT One-Larva-per-ontainer Mosquito Surveys onduted in Bangkok-Thonburi, Thailand, in 1969* by ROBRT J. To 1 & Y. H. BAG2 One-larva-per-ntainer surveys have been nduted in Bangkok sine 1966. Tonn et

More information

Optimizing the Allocation of Marketing Promotional Contacts

Optimizing the Allocation of Marketing Promotional Contacts Optimizing the Alloation of Marketing Promotional Contats Keith Hermiz, Ph.D., IBM Helene Miller, IBM Dhanesh Padmanabhan, Marketis Tehnologies Abstrat The typial marketing environment in the business-to-business

More information

Nonhomothetic Preferences and International Trade

Nonhomothetic Preferences and International Trade Abstratroie_876 408..426 Review of International Eonomis, 18(2), 408 425, 2010 DOI:10.1111/j.1467-9396.2010.00876.x Nonhomotheti Preferenes and International Trade Jeffrey J. Reimer and Thomas W. Hertel*

More information

Stockholm recycling bin

Stockholm recycling bin 1/8 Stokholm reyling bin Reyling Bins Colletives Spaes Indoor/Outdoor Front Door Reyling Bin, Modularity & Unlimited Combinations Reyling bin of design, high performane & versions Upper sorting slots,

More information

The estimation of the cooling tower height by modeling the water and air contact situation in cooling tower falling film

The estimation of the cooling tower height by modeling the water and air contact situation in cooling tower falling film Journal of Cemial Engineering and Materials Siene Vol. 2(2), pp. 21-27, February 2011 Available online at ttp://www.aademijournals.org/jems ISSN-2141-6605 2011 Aademi Journals Full Lengt Resear Paper Te

More information

Bridge Element Deterioration Rates

Bridge Element Deterioration Rates TRANSPORTATION RESEARCH RECORD 149 9 Bridge Element Deterioration Rates lmad J. ABED-AL-RAHIM AND DAVID W. JOHNSTON Prediting the deterioration rates of bridge elements is an important?ponent of any ridge

More information

Small businesses work wonders for Pennsylvania in

Small businesses work wonders for Pennsylvania in A Message From The Senator Small businesses work wonders for Pennsylvania in fat, they are the mainstay of the Commonwealth's eonomy. However, starting up a new firm and trying to omply with state and

More information

Design of Corrugated Metal Box Culverts

Design of Corrugated Metal Box Culverts Transportation Researh Reord 18 33 Design of Corrugated Metal Box Culverts J. M. DUNCAN, R. B. SEED, and R. H. DRA WSKY ABSTRACT Corrugated metal box ulverts provide large ross-setional areas for water

More information

HIGH STRENGTH CONCRETE FOR SUSTAINABLE CONSTRUCTION

HIGH STRENGTH CONCRETE FOR SUSTAINABLE CONSTRUCTION 434 HIGH STRENGTH CONCRETE FOR SUSTAINABLE CONSTRUCTION Wu, D. 1, Sofi, M. 1 Mendis, P. 1 1 Department of Civil and Environmental Engineering, University of Melbourne, Vitoria, Australia. E-mail: d.wu11@ugrad.unimelb.edu.au

More information

Field Accuracy of Temperature Measurements in TAB Work Andrew P. Nolfo, PE

Field Accuracy of Temperature Measurements in TAB Work Andrew P. Nolfo, PE Field Accuracy of Temperature Measurements in TAB Work Andrew P. Nolfo, PE The purpose of this article is to discuss the measuring and reporting of temperatures at heat transfer equipment during the Testing

More information

Page 1 of 6 Searh All WHO This site only Home About WHO Countries Health topis Publiations Data and statistis Programmes and projets Food Safety Zoonoses Mirobiologial risks Chemial risks Biotehnology

More information

Design and development of a residential gas-fired heat pump

Design and development of a residential gas-fired heat pump Design and development of a residential gas-fired heat pump Edward A Vineyard a*, Ahmad Abu-Heiba a, Isaac Mahderekal b a Oak Ridge National Laboratory, P.O. Box 2008, MS 6070, Oak Ridge, TN, 37831, USA

More information

EVOLUTION OF ANNEALING TWINS IN SPUTTERED CU THIN FILMS CHANG-KYU YOON. A thesis submitted in partial fulfillment of the requirement for the degree of

EVOLUTION OF ANNEALING TWINS IN SPUTTERED CU THIN FILMS CHANG-KYU YOON. A thesis submitted in partial fulfillment of the requirement for the degree of EVOLUTION OF ANNEALING TWINS IN SPUTTERED CU THIN FILMS By CHANG-KYU YOON A thesis submitted in partial fulfillment of the requirement for the degree of MASTER OF SCIECE I MATERIALS SCIECE AD EGIEERIG

More information

TI /3 Tinbergen Institute Discussion Paper Second-best Road Pricing Through Highway Franchising

TI /3 Tinbergen Institute Discussion Paper Second-best Road Pricing Through Highway Franchising I 2005-082/3 inbergen Institute Disussion Paper Seond-best Road Priing hrough Highway Franhising Erik Verhoef Department of Spatial Eonomis, Free niversity Amsterdam, and inbergen Institute. inbergen Institute

More information

PROPERTIES OF SRP COMPOSITES AND THEIR EFFECT ON DESIGN PROCEDURES

PROPERTIES OF SRP COMPOSITES AND THEIR EFFECT ON DESIGN PROCEDURES PROPERTIES OF SRP COMPOSITES AND THEIR EFFECT ON DESIGN PROCEDURES Rafał Krzywoń PhD MsC Silesian University of Tehnology, Poland rafal.krzywon@polsl.pl Summary Desribed in the paper omposites are based

More information

Numerical Simulation of Combustion Chamber for Button Turbojet Engine

Numerical Simulation of Combustion Chamber for Button Turbojet Engine Numerial Simulation of Combustion Chamber for Button Turbojet Engine Hongpeng Ma, Shuzhou Fang, Hang Gao, Teng Li and Guanlin Fang Shool of Aerospae Siene and Engineering, Beijing Institute of Tehnology,

More information

The fracture of a Al bicycle crank arm.

The fracture of a Al bicycle crank arm. The frature of a Al biyle rank arm. Failure In hapters 6 and 7 we examined the elasti and plasti behaviour of materials. We learned how the motion of disloations makes it possible for the material to deform.

More information

Human Capital Externalities and Growth of High- and Low-Skilled Jobs

Human Capital Externalities and Growth of High- and Low-Skilled Jobs DISCUSSION PAPER SERIES IZA DP No. 1969 Human Capital Externalities and Growth of High- and Low-Skilled Jobs Jens Suedekum February 2006 Forshungsinstitut zur Zukunft der Arbeit Institute for the Study

More information

Modelling the Stress-Strain Behaviour for Aluminum Alloy AA6111

Modelling the Stress-Strain Behaviour for Aluminum Alloy AA6111 Proeedings of the 9 th International Conferene on Aluminium Alloys (4) Edited by J.F. Nie, A.J. Morton and B.C. Muddle Institute of Materials Engineering Australasia Ltd 939 Modelling the Stre-Strain Behaviour

More information

Organizations engage in search whenever they perform nonroutine tasks, such as the definition and validation

Organizations engage in search whenever they perform nonroutine tasks, such as the definition and validation MANAGEMENT SCIENCE Vol. 5, No. 5, May, pp. 3 4 issn 5-99 eissn 5-55 55 3 informs doi.7/mns..4 INFORMS Hierarhial Struture and Searh in Complex Organizations Jürgen Mihm, Christoph H. Loh INSEAD, 7735 Fontainebleau

More information

The Participants in this GreenON Rebates Program are homeowners and landlords.

The Participants in this GreenON Rebates Program are homeowners and landlords. Program Name: GreenON Rebates Program 1. Program Description The GreenON Rebates Program is designed to encourage homeowners to invest in building envelope and HVAC upgrades to help reduce energy costs,

More information

Two-Way Flat Slab (Concrete Floor with Drop Panels) System Analysis and Design

Two-Way Flat Slab (Concrete Floor with Drop Panels) System Analysis and Design Two-Way Flat Slab (Conrete Floor with Drop Panels) System Analysis and Design Two-Way Flat Slab (Conrete Floor with Drop Panels) System Analysis and Design Design the onrete floor slab system shown below

More information

Non-linear Predictive Control of a Fermentor in a Continuous Reaction-separation Process

Non-linear Predictive Control of a Fermentor in a Continuous Reaction-separation Process , Otober 9-2, 20, San Franiso, USA Non-linear Preditive Control of a Fermentor in a Continuous Reation-separation Proess Edwin G. Boza-Condorena, Daniel Ibraim Pires Atala, and Aline Carvalho da Costa

More information

CALIFORNIA INSTITUTE OF TECHNOLOGY

CALIFORNIA INSTITUTE OF TECHNOLOGY VSON OF THE HUMANTES AN SOCAL SCENCES CALFORNA NSTTUTE OF TECHNOLOGY PASAENA, CALFORNA 91125 COSTLY OFFERS AN THE EQULBRATON PROPERTES OF THE MULTPLE UNT OUBLE AUCTON UNER CONTONS OF UNPRECTABLE SHFTS

More information

Active and Reactive Power Control of a Variable Speed Wind Energy Conversion System based on Cage Generator

Active and Reactive Power Control of a Variable Speed Wind Energy Conversion System based on Cage Generator Vol. 8 No. 9 7 Ative and Reative Power Control of a Variable Speed Wind Energy Conversion System based on Cage Generator Mazhar Hussain Baloh Engineering MUET Khairpur Mir s Campus Pakistan Waqas Ahmed

More information