Experimental Exergetic Performance Evaluation of an Elevator Air Conditioner Using R-1234yf

Transcription

1 IACSIT Internatonal Journal of Engneerng and Technology, Vol. 7, No., June 5 Expermental Performance Evaluaton of an Elevator Ar Condtoner Usng R-yf M. Araz, A. Güngör, and A. Hepbasl Abstract In ths study, an evator ar condtonng (EAC) prototype, desgned and manufactured at a factory located n Izmr, Turkey, s consdered to assess ts performance usng ergy analyss method. The analyses performed nclude to varous refrgerants, namy R-a and R-yf. The maxmum mprovement potental s found to be n the condenser for R-a, hle t s n the ressor for R-yf. The COP values are determned to be.55 and., hle the product/fu based ergy effcences are determned to be 58.7% and 57.9% for R-a and R-yf, respectvy. The bggest rreversblty occurred n the ressor for both refrgerants. The ergy loss and flo dagram (the so-called Grassmann dagram) s also presented for the EAC studed to gve quanttatve nformaton regardng the proporton of the ergy nput that s dsspated n the varous system onents. Ind Terms Elevator ar condtonng, ergy analyss, R-yf, R-a. I. INTRODUCTION Refrgeraton hstory goes back to ancent tmes, here stored ce, vaporzaton of ater and other evaporatve processes are used. In the 8s, Perkns has nvented the frst vapor resson machne and ntroduced us th the refrgerants. At those tmes every flud that orks and as avalable as used. After that the specfcatons that e ant from a refrgerant shoed changes th tme. Today, refrgerants should have zero ozone depleton potental (ODP), lo global armng potental (GWP), short atmospherc lfetme and hgh effcency, as a consequence of the legslatons, namy the Kyoto Protocol, the F-Gas Regulaton and MAC (moble ar condtonng) Drectve, hch have come nto force []. Especally the MAC Drectve [] puts some certan restrctons to the use of refrgerants n moble ar condtonng systems. Accordng to ths drectve, refrgerants th a GWP of hgher than 5 shall not be used n all ne vehcle mods startng from January and th effect from January 7 n all ne vehcles. The mmedate effect of ths regulaton s the ban of R-a n MACs, here t s mostly used. Recently (on th of March) European Parlament has formally adopted the ne F-Gas Regulaton [], hch has put strct restrctons to refrgeraton applcatons rated to the use of HFC Manuscrpt receved Aprl 5, ; revsed June 6,. Ths ork as supported n part by the Republc of Turkey Mnstry of Scence, Industry and Technology under the SAN-TEZ program. M. Araz and A. Hepbasl are th the Department of Energy Systems Engneerng, Yasar Unversty, 5 Bornova, İzmr, Turkey (e-mal: {mustafa.araz, arf.hepbasl}@yasar.edu.tr) A. Güngör s th the Department of Mechancal Engneerng, Ege Unversty, 5 Bornova, İzmr, Turkey (e-mal: al.gungor@ege.edu.tr). refrgerants. Bans on HFCs n ne equpment accordng to ths regulaton are lsted bo. Domestc refrgerators and freezers that contan HFCs th GWP 5 as of January 5, Refrgerators and freezers for commercal use (hermetcally sealed equpment) that contan HFCs th GWP 5 as of January and HFCs th GWP 5 as of January, Movable room ar-condtonng equpment (hermetcally sealed equpment hch s movable beteen rooms by the end user) that contan HFCs th GWP 5 as of January, Sngle splt ar-condtonng systems contanng less than kg of fluornated greenhouse gases, that contan, or hose functonng res upon, fluornated greenhouse gases th GWP 75 as of January 5. As a consequence of all these restrctons, utlzaton of varous envronmentally frendly alternatve refrgerants th lo GWP has become essental. These alternatves can be dvded nto three man groups as follos: () HFCs th a GWP of less than 5 (e.g. R-5a), () Natural refrgerants (such as ammona, carbon doxde and hydrocarbons), and () Ne refrgerants (HFOs lke R-ze, R-yf). R-yf, also called as HFO-yf, s a ne refrgerant devoped by jont ork of Honeyl and DuPont to replace R-a n MAC systems. It has smlar thermophyscal propertes to R-a, thus can be used thout any equpment changes or th some mnor changes. It has clent envronmental propertes th a ODP value of, GWP of and atmospherc lfetme of days []. Because R-yf s a ne refrgerant, numerous studes on ts thermodynamc propertes, safety, stablty and performance have been performed by varous researchers, producers and automoble ndustry. In ths regard, Tanaka and Hgash [5] measured the thermodynamc propertes of R-yf. They calculated the vapor and lqud denstes by the Peng-Robnson and Hanknson-Thomson equatons hle the heat of vaporzaton as also determned. They concluded that almost all thermodynamc propertes of R-yf ere loer than those of R-a. Because safety s the key factor for the acceptance of a ne refrgerant, numerous tests and rsk assessments ere conducted regardng ts flammablty, toxcty. The results of the rsk assessment ere presented n the report prepared by Leandosk for SAE Internatonal Cooperatve Research Program CRP- [6]. Accordng to the report, the estmated probablty of vehcle occupant beng posed to a vehcle fre due to R-yf gnton (due to leak and gnton n engne artment) as - (probablty per vehcle per operatng hour). Koban [7] presented the results DOI:.776/IJET.5.V7.8 5

2 IACSIT Internatonal Journal of Engneerng and Technology, Vol. 7, No., June 5 rated to materal atblty, stablty and also mscblty n ols of R-yf. She reported that SAE CRP- and JAMA results ndcated good atblty and thermal stablty th varous commercally avalable common automotve materals hle R-yf as more mscble th POE lubrcants than R-a. Ikegam et al., [8] used lfe cycle clmate performance (LCCP) method to evaluate the envronmental performance of R-yf n arson th R-7. Based on the results reported, the use of R-yf ould lead to a % decrease n CO emssons n 7 th the assumpton of % alternatve refrgerant usage. On the other hand, n a report prepared by Kauffd [9], t s stated that there are concerns rated to the effects of the use of HFOs (hydrofluoroolefns) on large scale, regardng the envronment. In a study carred out by Jarahnejad [], the performance of R-yf as ared to that of R-a at dfferent heat load rates beteen kw and. kw. Accordng to the test results, R-a had n average -% hgher volumetrc coolng capacty hle R-yf had -8% loer volumetrc resson ork at condensng temperatures of C and. The COP value of R-a as n average -5% hgher than that of R-yf. R-a also shoed better performance n terms of heat transfer coeffcent. In another permental study performed by l-knon automoble manufacturers, the performance of R-yf has been nvestgated on a vehcle. In the drop-n tests, R-yf had a COP value of.8 hle the COP of R-a as.. After the optmzaton of the system (ncreasng subcoolng by % and thermal panson valve settng from bars to. bars), R-yf reached the lev of R-a n terms of COP []. There are also studes on ne devopmental refrgerants (DR), hch are manly mxtures of R-yf and other refrgerants. The am of DRs s to ncrease the performance of the system hle keepng the GWP under a certan lev at the same tme. Leck [] devoped a theoretcal refrgeraton cycle mod to sho the performance and envronmental characterstcs of DRs and ared ther capactes and COPs to that of R-A. All the ne blends presented a better COP value than that of R-A hle the capactes and GWP values ere loer. Exergy analyss s a very effectve tool n evaluatng system performance and optmzng energy savngs. In ths regard, varous studes have been conducted rated to heat pumps and refrgeraton systems. Hepbasl [] appled ergy modng to a solar asssted domestc hot ater tank ntegrated ground-source heat pump (GSHP) system. The ergy effcences on a product/fu bass ere found to be 7.% for the GSHP,.5% for the solar domestc hot ater system and.6% for the hole system. Ahamed et al., [] reveed ergy analyss of vapor resson refrgeraton systems n ther study. They nvestgated the effect of refrgerant on ergy analyss/parameters, and the effects of evaporatng and condensng temperatures, reference state, lubrcant and addtves on ergy losses. They concluded that major ergy losses are occurred n the ressor among the onents of the vapor resson system. Özgür et al., [] theoretcally nvestgated energetc and ergetc performance of R-a n arson th R-yf. They concluded that there ere not any mportant dfferences beteen ergy effcences of both refrgerants. R-yf as handled n more detal n prevous studes [5], [6] and therefore no nformaton rated to ts man propertes ll be gven here. The man objectve of ths contrbuton s permentally nvestgate the performance of an evator ar condtoner (EAC) prototype, desgned and manufactured at a factory located n Izmr, Turkey. To dfferent refrgerants, R-a and the ne LGWP refrgerant R-yf, have been tested on the prototype thout makng any changes on the system. Energy and ergy analyses of the system are performed and the obtaned results are ared to each other. II. EXPERIMENTAL SET-UP A. Test Faclty The perments have been conducted at the performance test faclty of the factory, as shon n Fg.. The test faclty conssts of to separate parts to smulate outdoor and ndoor envronments. The outdoor room dmensons are 5m m 6.5 m hle there s a m test car nsde, hch can be dvded nto smaller volumes usng separators. Insde the outer room, there are refrgeraton devces, each th a capacty of.5 kw and a.87 kw burner. Usng these devces, t s possble to reach temperatures beteen - C and +55 C. In ths study, an m nner volume has been used. The outdoor room temperature as set to 5 C±. Because there ere not any temperature and humdty control devces n the nner room, the tests have been conducted startng th an ndoor temperature of 5 C decreasng th tme. To mantan a ratvy smaller decrease, an nternal heat gan rate of kw as mantaned by usng an ectrcal heater. (a) (b) Fg. (a). Outdoor test room (b). Inner test room (th the permsson of SAFKAR INC.). B. Test Procedure The performance parameters, namy the pressure drop, the coolng capacty, the energy consumpton and the COP, ere calculated usng the data collected from the refrgerant sde. The temperatures of the refrgerant ere measured contnuously at the nlets and ts of the heat changers usng four PT- sensors and recorded th a data logger. The pressures at the nlet and outlet of the evaporator ere measured and recorded every seconds th an ectronc manfold. The pressures at the nlet and t of the condenser ere measured th an ectronc manfold, but recorded manually every 5 mnutes. The ndoor and outdoor ar temperatures ere also measured th PT- sensors and recorded th the data logger contnuously. The measurement devces used durng the perments and ther 55

3 IACSIT Internatonal Journal of Engneerng and Technology, Vol. 7, No., June 5 uncertantes are gven n Table I. The measurement ponts on the system and a pcture of the prototype mounted on the roof of the test room are gven n Fg. (a) and Fg. (b), respectvy. h h (c) The mechancal-ectrcal losses can be obtaned from: Measurement Devce TABLE I: UNCERTAINTIES Uncertanty PT ±. C Testo 57- Dgtal Manfold (Evaporator nlet and outlet pressures) Testo 557- Dgtal Manfold (Condenser nlet and outlet pressures) ±.5% ±.5% Wth dest, mech, ( m η ), η (d) h h η η (e) m The nternal rreversblty due to the flud frcton s calculated from:,nt, mech, (f) Condenser: (a) (b) Fg.. (a). Test schematc (b). Prototype mounted on the roof of the nner test room. C. Modlng The follong assumptons are made for energy and ergy analyses of the system. All processes are steady state and steady flo th neglgble potental and knetc energy effects. The pressure losses n the ppnes connectng the onents are neglgble, snce ther lenghts are short. Heat losses/gans beteen the envronment and system onents are gnored. The permental data used n the calculatons are average values durng the hole test perod. The thermodynamc propertes of the refrgerants are obtaned usng the Refprop softare package, devoped by NIST [7]. Snce there are not any flometers nstalled n the system to measure the mass flo rate of the refrgerant, all the obtaned results are on the unt mass bass. The mechancal (η m ) and ectrcal effcences (η ) of the ressor are taken to be.85 and.9, respectvy. The poer consumptons of the condenser and evaporator fans are assumed to be neglgble. Hgh and lo temperature are taken as the averages of the test perod, hch are 5 and 7, respectvy. The values for the reference state temperature and pressure are taken to be C and.5 kpa, respectvy. General energy, entropy and ergy balance equatons are reduced to specfc equatons for each onent llustrated n Fg. and are gven bo []. Compressor: h h (a) T s s + (b) ( ) q H h h (a) q H T + cond T s s qh (b) TH TH cond q Expanson valve: Evaporator: H ( T / T ) H cond (c) h h (a) ( s ) dest (b), p T s p (c) q L (a) h h q L T + + evap T s s ql (b) TL TL evap q H ( T T ) / T L L evap ( ) h h T s s (c) (5) The COP of the refrgeraton cycle can be calculated usng (6), hle the COP of the system ncludng mechancal and ectrcal losses can be determned from (6b): COP ql cycle (6a) 56

4 IACSIT Internatonal Journal of Engneerng and Technology, Vol. 7, No., June 5 COP ql system (6b) The overall ergy effcency based on product/fu bass can be calculated from: Total specfc ergy destructon can be derved from: tot + cond + p + evap () cycle specfc ergetc product specfc ergetc fu (7a) The functonal ergy effcency of the system may also be calculated usng: func (7b) Van Gool s mprovement potental on unt mass bass s gven by: ( )( ) p n out (8) Ratve rreversblty values for each onent can be obtaned from: RI (9) tot p f TABLE II: AVERAGE PRESSURE VALUES OF THE REFRIGERANTS III. RESULTS AND DISCUSSION The pressure values at the nlet and t of the evaporator and condenser, the pressure drop n each heat changer and the resson rato are also calculated and gven n Table II, hch are based on the average values taken durng the hole test perod. The pressure of R-yf s slghtly hgher than that of R-a for the evaporator and loer for the condenser hle ts resson rato s approxmaty % loer. Pressure-enthalpy and temperature-entropy dagrams of both refrgerants are llustrated and ared to each other n Fg. and Fg., respectvy. As t can be seen n Fg., the specfc coolng capacty of R-a s sgnfcantly hgher than that of R-yf hle ts specfc resson ork s slghtly loer than that of R-yf. The loer resson ork of R-yf causes an mprovement n the COP of the system. The dfference beteen the COP values of the to systems s, therefore, thn the range of 9%. Pressure (kpa) Pressure Drop (kpa) Compresson Rato Refrgerant Evap. Inlet Evap. Outlet Cond. Inlet Cond. Outlet Evaporator Condenser R-a R-yf Fg.. Ln P h dagram arson of R-a and R-yf. Table III for both refrgerants, hle Table IV presents some energetc and ergetc data for the system based on the specfc values. The ectrcal ork nput ( ) s calculated from (e) and found to be 6.5 kj/kg for R-a and 5.75 for R-yf. The greatest rreversblty/ergy destructon occurs on the ressor of the system for both refrgerants and t s folloed by the condenser, evaporator and the panson valve. The rreversblty rated to panson valve s ratvy very small and t s due to the pressure drop of the refrgerant. In terms of ergy effcences the follong nequalty can be rtten for both refrgerants: p > > cond > evap Fg.. T s dagram dagram arson of R-a and R-yf. Temperature and pressure values and correspondng specfc enthalpy, entropy and ergy values are lsted n Fg. 5. Exergy flo and loss (Grasmann) dagram for R-a. 57

5 IACSIT Internatonal Journal of Engneerng and Technology, Vol. 7, No., June 5 The overall ergy effcency values on product/fu bass for R-a and R-yf are found to be 58.7% and 57.9%, respectvy, hle the functonal ergy effcences are determned as 9.59% for R-a and 7.% for R-yf. Van Gool s mprovement potental gven n (8) s calculated for each onent of the refrgeraton system and the results are lsted n Table IV. It s found that for R-a, the ressor has the hghest ergetc mprovement potental (5.5 kj/kg) folloed by the condenser, evaporator and panson valve th.5, 9. and. kj/kg, respectvy. Smlarly, the hghest p value for R-yf occurred n the ressor due to ts hgh ergy destructon. The evaporator has an ergetc mprovement potental of 6.9 kj/kg, hch s very close to the value of the condenser (6.56 kj/kg). The p value of the panson valve for R-yf s found to be. kj/kg. One ay to see the results of ergy analyss s to dra ergy flo and loss (Grassmann) dagrams for the systems studed. In ths regard, the to Grasmann dagrams are dran for an ergy nput of % and llustrated n Fg. 5 and Fg. 6 for R-a and R-yf, respectvy. Fg. 6. Exergy flo and loss (Grasmann) dagram for R-yf. TABLE III: DATA USED IN THE ANALYSES State Evap. Comp. Cond. Exp. Descrpton - outlet/ outlet/ outlet/ outlet/ Comp. Cond.n Exp. Evap. nlet let nlet nlet Phase Flud Temperature, ( C) Pressure, (kpa) enthalpy entropy (kj/kg K) ergy Flud Temperature, ( C) Dead state Super heated vapor Super heated vapor R-a Saturat ed lqud Mxture R-yf Pressure, (kpa) enthalpy entropy (kj/kg K) ergy TABLE IV: RESULTS OF THE ENERGY AND EXERGY ANALYSES BASED ON SPECIFIC VALUES Flud R-a Component Evaporator Compressor Condenser Expanson valve Capacty product fu Exergy destructon Exergy effcency (%) mprovement potental Ratve rreversblty (%) COP of the system.55 Exergy effcency of the cycle (%) 58.7 Functonal ergy effcency of the system (%) 9.59 Flud R-yf Component Evaporator Compressor Condenser Expanson valve Capacty product fu Exergy destructon Exergy effcency (%) mprovement potental Ratve rreversblty (%) COP of the system. Exergy effcency of the cycle (%) 57.9 Functonal ergy effcency of the system (%) 7. IV. CONCLUSIONS An EAC unt s permentally nvestgated and t s performance s evaluated usng ergy analyses. The specfc ergy destructons, ergy effcences, ergetc mprovement potentals and ratve rreversbltes are 58

6 IACSIT Internatonal Journal of Engneerng and Technology, Vol. 7, No., June 5 calculated for each onent and arsons are made beteen the refrgerants. Some concludng remarks can be lsted as follos: The legslatons rated to the contrbuton of the stng refrgerants to global armng make t necessary to use alternatve refrgerants th lo GWP, such as R-yf. R-a shoed a slghtly better performance n drop-n tests. The coolng effect of R-yf s found to be approxmaty % loer, hle the resson ork of R-a s about % hgher than that of R-yf on the bass of the specfc enthalpy values. The loer resson ork causes an mprovement n the COP. The COP values of R-a and R-yf are.55 and., respectvy. R-yf has hgher pressure values than R-a for both heat changers. Whle the pressure drop values n the evaporator and condenser are 58.6 kpa and. kpa for R-yf, they are 5 and 8.7 for R-a, respectvy. No mportant dfference s found beteen the ergy effcences of the refrgerants. The ergetc effcency values based on product/fu bass are found to be 58.7% and 57.9% for R-a and R-yf, respectvy. On the other hand the functonal ergy effcences are 9.59% for R-a and 7.% for R-yf. For a further ork, t s recommended to conduct more tests th a refrgerant flometer to get the ergetc parameters on rate bass. Addtonally, ergoenvronmental analyss can be performed to assess the envronmental benefts of R-yf n arson th R-a. Exergoecomomc analyss may also be performed to sho the effect of the hgh cost of R-yf, hch s due to the nsuffcent producton capacty. ACKNOWLEDGMENT The authors are very grateful to the Republc of Turkey Mnstry of Scence, Industry and Technology for the support gven to ths project through the program called SAN-TEZ. They also thank DuPont for provdng a free sample of R-yf and R&D personn of SAFKAR INC., Izmr, Turkey for ther support and hp durng performng the tests. REFERENCES [] J. M. Calm, The nt generaton of refrgerants Hstorcal reve, consderatons, and outlook, Internatonal Journal of Refrgeraton, vol., pp. -, 6. [] Drectve 6//EC of the European Parlament and of the Councl of 7 May 6 Ratng To Emssons from Ar-Condtonng Systems n Motor Vehcles And Amendng Councl Drectve 7/56/EEC, Offce Journal of the Europan Unon, 6. [] The European Parlament. European Parlament legslatve resoluton of March on the proposal for a regulaton of the European Parlament and of the Councl on fluornated greenhouse gases (COM()6 C7-7/ /5(COD)). [Onlne]. Avalable: eenhouse_gases_en.pdf. [] M. Jarahnejad, Ne lo GWP synthetc refrgerants, Master of Scence Thess, Industral Engneerng and Management, KTH, Stockholm,. [5] K. Tanaka and Y. Hgash, Thermodynamc propertes of HFO-yf (,,, -tetrafluoropropene), Internatonal Journal of Refrgeraton, vol., pp. 7-79,. [6] T. A. Leandosk, Addtonal rsk Assessment of Alternatve Refrgerant R-yf,, pp. -9. [7] M. Koban, Automotve materal nvestgaton th lo GWP refrgerant HFO-yf, n Proc. Vehcle Thermal Management Systems Conference and Exhbton (VTMS), Wllmngton, DE,, pp. -8. [8] T. Ikegam, M. Iguch, K. Aok, and K. Ijma, Ne refrgerants evaluaton results, presented at the SAE 8 Alternate Refrgerant Systems Symposum, Arzona, 8. [9] M. Kauffd, Avalablty of Lo GWP Alternatves to HFCs-Feasblty of an early Phase-Out of HFCs by, Envronmental Investgaton Agency, Inc.,. [] R. Monforte, B. Rose, and J. -M. L Huller, Updated stuaton about alternate refrgerant evaluaton, presented at the SAE 8 Alternate Refrgerant Systems Symposum, Scottsdale, AZ, 8. [] T. J. Leck, Ne hgh performance lo GWP refrgerants for statonary AC and refrgeraton, n Proc. Internatonal Refrgeraton and Ar Condtonng Conference, Purdue,, pp. -8. [] A. Hepbasl, modng and assessment of solar asssted domestc hot ater tank ntegrated ground-source heat pump systems for resdences, Energy and Buldngs, vol. 9, pp. -7, 7. [] J. U. Ahamed, R. Sadur, and H. H. Masjuk, A reve on ergy analyss of vapor resson refrgeraton system, Reneable and Sustanable Energy Reves, vol. 5, pp. 59-6,. [] A. E. Özgür, A. Kabul, and Ö. Kzlkan, Exergy analyss of refrgeraton systems usng an alternatve refrgerant (HFO-yf) to R-a, Internatonal Journal of Lo-Carbon Technologes, vol. 9, pp. -7,. [5] M. Araz, A. Güngör, H. Yaldırak, and H. G. Özcan, Utlzaton possbltes of R-yf n automoble ndustry, n Proc. st Natonal Ar Condtonng Refrgeraton Educaton Symposum and Exhbton,. (n Turksh) [6] M. Araz, A. Güngör, and A. Hepbasl, Assessment of the use of Lo Global Warmng Potental (LGWP) refrgerants n refrgeraton applcatons, n Proc. th Natonal HVAC and Santary Conventon and Exhbton (TESKON ),, vol., pp (n Turksh) [7] E. W. Lemmon, M. L. Huber, and M. O. McLnden, NIST Standard Reference Database : Reference Flud Thermodynamc and Transport Propertes-REFPROP, verson 9., Natonal Insttute of Standards and Technology, Standard Reference Data Program, Gathersburg,. M. Araz as born n Karaman, Turkey on August, 986. He receved B.S. degree n mechancal engneerng from Ege Unversty, Turkey n, M.S degree n and s currently a Ph.D. student n mechancal Engneerng at Ege Unversty. He leted hs mltary servce n. He has been orkng as a research assstant n the Energy Systems Engneerng Department of Yaşar Unversty, n İzmr, snce October,. He has orked as scholarshp student n the project enttled Desgn of an Elevator Ar Condtonng Unt Usng R-yf, hch s supported by the Republc of Turkey Mnstry of Scence, Industry and Technology. Hs research nterests are lo global armng potental (LGWP) refrgerants, ar condtonng systems, refrgeraton technologes and clean energy systems. Mr. Araz s a member of Unon of Chambers of Turksh Engneers and Archtects the Chamber of Mechancal Engneers. A. Güngör as born n Elazığ, Turkey n 955 and has to daughters. He receved B.S n mechancal engneerng n 977 and M.S. n 978 from the Department of Mechancal Engneerng of Ege Unversty, Turkey and a Ph.D. n 985 from the Solar Energy Insttute of the same unversty. He conducted research at the Brace Research Insttute, Canada n 986 for 6 months. He became an assocate professor n the fd of Heat and Mass Transfer n 989 and a professor n 996 at Ege Unversty. He has orked n dfferent nsttutons ncludng Department of Mechancal Engneerng of Dokuz Eylül Unversty, Solar Energy Insttute and Department of Mechancal Engneerng of Ege Unversty snce 978. He as the head of the Department of Mechancal Engneerng of Ege Unversty beteen 997 and and s stll servng at the same department as the head of Thermodynamcs Dvson. Hs research nterests are ar condtonng, solar thermal energy applcatons, refrgeraton technque, absorpton and adsorpton refrgeraton technologes, dryng technque, heat ppes, thermodynamcs and heat and mass transfer applcatons. Professor Güngör s a member of Unon of Chambers of Turksh Engneers and Archtects the Chamber of Mechancal Engneers, Turksh Heat Scence and Technque Assocaton and ASHRAE. 59

7 IACSIT Internatonal Journal of Engneerng and Technology, Vol. 7, No., June 5 A. Hepbasl as born n Izmr, Turkey on June 7, 958. He receved B.S. (frst class honor) n mechancal engneerng from Scuk Unversty (SU), Turkey n 98, M.S. from Istanbul Techncal Unversty of Istanbul, Turkey n 985 and a Ph.D. n mechancal engneerng from Scuk Unversty n 99 hle he as orkng n ndustry. He joned Ege Unversty n 996 after about a ten-year perod n ndustry at dfferent postons and a one-year perod at Izmr Branch Offce of Chamber of Mechancal Engneers as a consultant. He has been apponted as the Head of Energy Systems Engneerng Department at Yaşar Unversty n Izmr, Turkey snce September. He s the author and co-author of over 5 papers (over 5 SCI-based papers th an h-nd of ) on a natonal and nternatonal bass as l as several natonal and nternatonal books and book chapters. Hs research has been nvolved th energy, ergy, ergoeconomc and ergoenvronmental analyses and assessments of energy-rated systems, energy/ergy effcency and management, clean energy technologes, ground-source heat pumps, utlzaton and potental of reneable energy sources and sustanable energy technologes. He has served as a consultant for ndustry n cases nvolvng hs research area and s also a member n the nternatonal advsory board of eght prestgous energy-rated journals, and an assocate edtor of Journal of Energy Engneerng (ASCE) hle also servng many energy journals and ndustral projects as a reveer. 6