UNCERTAINTY ON PERFORMANCE MEASUREMENT OF S-CO 2 COMPRESSOR OPERATING NEAR THE CRITICAL POINT
|
|
- Lesley O’Connor’
- 6 years ago
- Views:
Transcription
1 UNCERTAINTY ON PERFORMANCE MEASUREMENT OF S-CO COMPRESSOR OPERATING NEAR THE CRITICAL POINT The 4th International Symposium - Supercritical CO Power Cycles September 9-10, 014, Pittsburgh, Pennsylvania Jekyoung Lee a, Seong Gu Kim a, Jeong Ik Lee a, Jae Eun Cha b a Korea Advanced Institute of Science and Technology b Korea Atomic Energy Research Institute
2 CONTENTS Introduction Uncertainty analysis Summary and further works
3 Introduction S-CO Brayton cycle development in KAIST research team Steam Rankine Cycle S-CO Brayton Cycle Economic benefit due to higher efficiency and compactness of power conversion system Difficulties on S-CO Brayton cycle Dramatic change on thermodynamic properties near the critical point Compressor Design methodology C p (kj/kg K) MPa 7.4 MPa 7.5 MPa 7.6 MPa 7.7 MPa 7.8 MPa 7.9 MPa 8 MPa Temperature ( O C) 3
4 Introduction S-CO Pressurization Experiment (SCOPE, constructed in KAIST) Components 1. Overview. Impeller 3. Main compressor 4. Pre-cooler 5. Booster pump 6. Vacuum pump Sensors PT100 Ohm RTDs Static temperature Rosemount 3051S Pressure Transmitter Static pressure Rheonik RHM0 mass flow meter Accuracy Sensor type Accuracy RTD ±0. o C Pressure transmitter ±0.09% Mass flow meter ±0.16% RPM ±0.1% Power ±0.5kW 4
5 Introduction Main compressor description TE PT Hot water Motor HS Vent Cold water PSV Main Main Compressor Pump PT FE TE HS PT Vent TE TE Heat exchanger Water Line Hot water TE Cold water Canned motor pump 6kW motor driver Sleeve journal bearing with working fluid lubrication Closed(shrouded) type impeller Recirculation flow exists Water jacket is equipped to maintain integrity of sleeve bearing Available RPM: 460(77Hz) S-CO Line Charging system Main compressor design conditions Inlet pressure, MPa Outlet pressure, MPa Pressure ratio 1.18 RPM 448 Mass flow rate, kg/s 4.49 Dimensions of mechanical parts Impeller type Closed Impeller diameter, mm 34 Journal bearing type Sleeve Thrust bearing type Plain Material SUS316 5
6 Introduction SCOPE operation purpose. 1 Experience to CO pressurization with various fluid conditions SCOPE operation purpose. V&V of KAIST_TMD Turbomachinery in-house code SCOPE operation purpose. 3 V&V of KAIST_HXD Heat exchanger in-house code Total to Total Efficiency (%) Turbomachinery Efficiency-Mdot Map On-design point rpm=3600 rpm=4500 rpm=5400 rpm=6300 rpm=700 Pressure Ratio Turbomachinery PR-Mdot Map On-design point rpm=700 rpm=6300 rpm=5400 rpm=4500 rpm= Mass Flow Rate (kg/s) Mass Flow Rate (kg/s) 6
7 Uncertainty Analysis Compressor performance variable Pressure ratio Isentropic efficiency hout, ideal h 1: η = h h : PR = P P η = out in out in in ( ho, out, isen ho, in ) m W Nomenclature PR : pressure ratio η : efficiency h : enthalpy m : mass flow rate W : input power U : impeller tip speed in : compressor inlet out : compressor outlet isen : isentropic process o : stagnation th : theoretical (Euler equation) loss : loss in compressor int : internal loss ext : external loss 3: h h h m th loss, int th U η = =,(where, hloss, ext >> loss, int ) hth + hloss, ext hth + hloss, ext W Internal losses : Losses occurred through primary paths of working fluid in a machinery External losses : Losses generated from the exterior of primary paths Primary path 7
8 Uncertainty Analysis Nomenclature h : enthalpy Uncertainty analysis m : mass flow rate Relative(fractional) uncertainty [] W : input power 1/ ω f 1 f U : impeller tip speed in : compressor inlet = ϖ x i out : compressor outlet f f x i isen : isentropic process Pressure ratio o : stagnation 1/ ω : uncertainty ω PR o ωp ω o, out P o, in = + PR o P o, out P o, in Isentropic efficiency ω η 1 ho, out, isen h o, out ( 1) 1: = ωh + ω o, isen h + ω oin, h o, out η ho, out, isen h o, in ( ho, out ho, in )( ho, out, isen ho, in ) ho, out h o, in 1/ ω η : = ωh + ω o, out, isen h + ω oi, n m + ω W η ho, out, isen h o, in ho, out, isen h o, in m W 1/ ω η 1 1 3: = ωu ω + m + ω W η U m W 1/ [] Holman, J. P., 001, Experimental Methods for Engineers, McGraw-Hill, New York, NY, USA 8
9 Uncertainty Analysis Data cases Case 1, 83 bar, 40 o C, above the critical operation Case, 74.4 bar, 3.5 o C, near the critical operation Mass flow rate (kg/s) Inlet P (kpa) Outlet P (kpa) Inlet T ( o C) Outlet T ( o C) RPM Mass flow rate (kg/s) Inlet P (kpa) Outlet P (kpa) Inlet T ( o C) Outlet T ( o C) RPM Measured data Measured data Pressure (bar) Temperature ( o C) Case1 (.0kg/s) Case1 (1.5kg/s) Case1 (1.0kg/s) Case1 (0.5kg/s) Case (1.0kg/s) Case (1.5kg/s) Case (.0kg/s) Case (.8kg/s) 9
10 Uncertainty Analysis Uncertainty calculation results PR = η η = P P out in h -h out,ideal in = h out -h in ( ho, out, isen ho, in ) U η = W m m W Mass flow rate kg/s PR ωpr PR η ωη η ωη η ωη Case 1, Supercritical operation Case, Near the critical operation , (%) / η , (%) / η Time 0.53 (s) , (%) / η Efficiency (%) Efficiency / * 1 : Even near the steady ω η state, a large fluctuation 1 (50%-150% Range) of efficiency 1 was observed due to very small 1 background noise 1 in temperature and pressure measurement. Thus it is = not possible to report efficiency ωh based on + equation (3). ω o, out, isen h + ω oi, n m + ω W η ho, out, isen h o, in ho, out, isen h o, in m W 10
11 Uncertainty Analysis Issue 1 Peak region on property variation of S-CO near the critical point causes high uncertainty on efficiency measurement Inherent characteristic of S-CO near the critical point Strong correlation with specific heat and measurement uncertainties 11
12 Uncertainty Analysis SCOPE Recompression Layout Issue Performance measurement to low isentropic enthalpy rise (which is related with pressure ratio) compressor has high uncertainty on efficiency measurement for temperature and pressure measurement S-CO Integral Experiment Loop (SCIEL) 1
13 Uncertainty Analysis Issue 3 Applying of density measurement at compressor inlet and outlet reduces uncertainty on efficiency measurement [1]. T: Temperature, P: Pressure, D: Density Inlet : T P Outlet : T - P 1% Improvement Inlet : D P Outlet : T - P 33% Improvement Inlet : D P Outlet : D - P [1] Wahl, G. D., 009, "Efficiency Uncertainty of a Turbine Driven Compressor in a Supercritical CO Brayton Cycle", Proceedings of S-CO Power Cycle Symposium, RPI, Troy, NY 13
14 Uncertainty Analysis Issue 4 Approximation on efficiency calculation is necessary for low pressure ratio S-CO compressor with near the critical operation condition Due to uncertainty of enthalpy terms on efficiency calculation equations, high uncertainty always involves when S-CO compressor inlet condition is near the critical point Approximation on efficiency calculation for main compressor of SCOPE h h h m th loss, int th U η = = hth + hloss, ext hth + hloss, ext W 1 1 = ω + ω + ω η ω η U m W U m W 1/,(where, h >> ) loss, ext loss, int Out Basis Recirculation (High pressure) low specific speed design Some portion of high(discharge) pressure S-CO recirculates through shaft Thus, it is fair assumption that external losses are greater than internal losses High friction In It doesn t represent actual isentropic efficiency of machinery. However, it can be utilized for the base data for operation with low uncertainty 14
15 Uncertainty Analysis Issue Actual enthalpy input Approximation on efficiency calculation is necessary for low pressure ratio S-CO compressor with near the critical operation condition Due to uncertainty of enthalpy terms on efficiency calculation equations, high uncertainty always involves when S-CO compressor inlet condition is near the h critical point th + hext, loss Approximation on efficiency calculation for main compressor of SCOPE hth hloss, int hth U m η = = hth + hloss, ext hth + hloss, ext W 1 1 = ω + ω + ω η ω η U m W U m W Enthalpy (J/kg) 1/ 5000,(where, h >> ) h th loss, ext loss, int h ext, loss Evaluated enthalpy input Ideal enthalpy rise Out Recirculation (High pressure) High friction In Basis low specific speed design Mass flow rate (kg/s).5 3 Some portion of high(discharge) pressure S-CO recirculates through shaft Thus, it is fair assumption that external losses are greater than internal losses It doesn t represent actual isentropic efficiency of machinery. However, it can be utilized for the base data for operation with low uncertainty 15
16 Summary and further works Issues on uncertainty on efficiency measurement of near the critical operation S-CO compressor 1. Peak region on property variation of S-CO near the critical point causes high uncertainty on efficiency measurement Inherent characteristics of S-CO near the critical point. Performance measurement on low isentropic enthalpy rise (which is related with pressure ratio) compressor has high uncertainty on efficiency measurement Machine dependency At.7 pressure ratio, this issue will be mitigated with under 0.1 of relative uncertainty. 3. Applying of density measurement at compressor inlet and outlet reduces uncertainty on efficiency measurement [1]. It is true that it increases measurement confidence. However it doesn t provide remarkable improvement for low pressure ratio S-CO compressor. 4. Approximation on efficiency calculation is necessary for low pressure ratio S-CO compressor with near the critical operation condition Just for SCOPE compressor which has relatively high external losses It doesn t represent actual efficiency but it can be used for performance indicator for operation with low uncertainty 16
17 Summary and further works Further works Uncertainty analysis for the compressor of S-CO Integral Experiment Loop (SCIEL) Construction field : Korea Atomic Energy Research Institute (KAERI) 014 construction : Simple cycle demonstration analysis on each loss model will be carried out to make better approximation on performance measurement. 17
18 THANK YOU..
Operation Results of a Closed Supercritical CO 2 Simple Brayton Cycle
Operation Results of a Closed Supercritical CO 2 Simple Brayton Cycle Jae Eun Cha Senior Researcher Korea Atomic Energy Research Institute Daejeon, Korea jecha@kaeri.re.kr Seong Won Bae Senior Researcher
More informationInstallation of the Supercritical CO 2 Compressor Performance Test Loop as a First Phase of the SCIEL facility
Installation of the Supercritical CO 2 Compressor Performance Test Loop as a First Phase of the SCIEL facility Jae Eun Cha a*, Yoonhan Ahn b, Je Kyoung Lee b, Jeong Ik Lee b, Hwa Lim Choi a a Korea Atomic
More informationS-CO 2 cycle design and control strategy for the SFR application
S-CO 2 cycle design and control strategy for the SFR application 2016. 03. 30 Yoonhan Ahn, Min Seok Kim, Jeong Ik Lee Ph.D. candidate. Dept. of Nuclear & Quantum Engineering, KAIST minskim@kaist.ac.kr
More informationCycle layout studies of S-CO 2 cycle for the next generation nuclear system application
Cycle layout studies of S-CO 2 cycle for the next generation nuclear system application Yoonhan Ahn* a, Seong Jun Bae a, Minseok Kim a, Seong Kuk Cho a, Seungjoon Baik a, Jeong Ik Lee *a, Jae Eun Cha b
More informationDesign considerations on a small scale supercritical CO 2 power system for industrial high temperature waste heat to power recovery applications
Design considerations on a small scale supercritical CO 2 power system for industrial high temperature waste heat to power recovery applications Giuseppe Bianchi a*, Savvas A. Tassou a, Yunting Ge a, Hussam
More informationChapter 6: Stationary Combustion Systems
Chapter 6: Stationary Combustion Systems Figure 6-1. Schematic of components of coal-fired electric plant, with conversion of coal to electricity via boiler, turbine, and generator US Energy Sources 2004
More informationCH 7: GAS-TURBINE ENGINES Prepared by Dr. Assim Al-Daraje BRAYTON CYCLE: THE IDEAL CYCLE FOR GAS-TURBINE ENGINES
CH 7: GAS-TURBINE ENGINES Prepared by Dr. Assim Al-Daraje BRAYTON CYCLE: THE IDEAL CYCLE FOR GAS-TURBINE ENGINES The combustion process is replaced by a constant-pressure heat-addition process from an
More informationDevelopment of A Transient Analysis Code for S CO2 Power Conversion System
Development of A Transient Analysis Code for S CO2 Power Conversion System ChunTian Gao, Pan Wu, JianQiang Shan, Bin Zhang School of Nuclear Science and Technology, Xi an Jiaotong University The 6 th Supercritical
More informationS-CO2 cycle design and control strategy for the SFR application
The 5 th International Symposium - Supercritical CO 2 Power Cycles March 28-31, 2016, San Antonio, Texas S-CO2 cycle design and control strategy for the SFR application Yoonhan Ahn Korea Advanced Institute
More informationPractice Final Exam (A) Six problems. (Open-book, HW solutions, and notes) (Plus /minus 10 % error acceptable for all numerical answers)
ME 3610 Practice Final Exam (A) Six problems. (Open-book, HW solutions, and notes) (Plus /minus 10 % error acceptable for all numerical answers) (18 points) 1. A gasoline engine operating on the ideal
More informationSteady State and Transient Modeling for the 10 MWe SCO 2 Test Facility Program
The 6 th International Symposium Supercritical CO 2 Power Cycles March 27-29, 2018, Pittsburgh, Pennsylvania Steady State and Transient Modeling for the 10 MWe SCO 2 Test Facility Program Megan Huang Principal
More informationChapter 9: Vapor Power Systems
Chapter 9: Vapor Power Systems Table of Contents Introduction... 2 Analyzing the Rankine Cycle... 4 Rankine Cycle Performance Parameters... 5 Ideal Rankine Cycle... 6 Example... 7 Rankine Cycle Including
More informationOff-design Performance of the Recompression sco2 Cycle for CSP Applications
Off-design Performance of the Recompression sco2 Cycle for CSP Applications 5 th International Supercritical CO2 Power Cycles Symposium Ty Neises -NREL Louis Tse -UCLA March 30, 2016 NREL is a national
More informationAlpha College of Engineering
Alpha College of Engineering Department of Mechanical Engineering TURBO MACHINE (10ME56) QUESTION BANK PART-A UNIT-1 1. Define a turbomahcine. Write a schematic diagram showing principal parts of a turbo
More informationComparison of micro gas turbine heat recovery systems using ORC and trans-critical CO 2 cycle focusing on off-design performance
Comparison of micro gas turbine heat recovery systems using ORC and trans-critical CO 2 cycle focusing on - performance IV International Seminar on ORC Power Systems September 13-15, 2017 Suk Young Yoon,
More information2. The data at inlet and exit of the turbine, running under steady flow, is given below.
3 rd week quiz 1. Identify the correct path of fluid flow in a steam power plant. a) Steam turbine-pump-boiler-condenser. b) Economizer- evaporator- superheater. c) Pump-turbine-condenser-evaporator. d)
More informationMethodology of Modeling and Comparing the Use of Direct Air-Cooling for a Supercritical Carbon Dioxide Brayton Cycle and a Steam Rankine Cycle
The 5 th International Symposium Supercritical CO2 Power Cycles March 28-31, 2016, San Antonio, Texas Methodology of Modeling and Comparing the Use of Direct Air-Cooling for a Supercritical Carbon Dioxide
More informationDynamic Modeling and Control of Supercritical CO 2 Power Cycle using Waste Heat from Industrial Process
12 th ECCRIA (European Conference on Fuel and Energy Research and its Applications) Dynamic Modeling and Control of Supercritical CO 2 Power Cycle using Waste Heat from Industrial Process Olumide Olumayegun,
More informationPower Recovery in LNG Regasification Plants
Power Recovery in LNG Regasification Plants Harry K. Clever Director of Sales hclever@ebaraintl.com Hans E. Kimmel Executive Director R&D hkimmel@ebaraintl.com Ebara International Corporation Sparks, Nevada,
More informationFEE, CTU in Prague Power Engineering 2 (BE5B15EN2) Exercise 3
Example 1: How is the applied heat for 1 kg of water steam at constant pressure p = 1.47 MPa, if the dryness of wet water is increased from x 1 = 0.8 to x 2 = 0.96? Dryness of wet steam the ratio of steam
More informationThe S-CO2 Brayton cycle code development and the thermal dynamic analysis of a small scaled facility
The 6th International Supercritical CO2 Power Cycles Symposium March 27-29, 2018, Pittsburgh, Pennsylvania The S-CO2 Brayton cycle code development and the thermal dynamic analysis of a small scaled facility
More informationR13. II B. Tech I Semester Regular/Supplementary Examinations, Oct/Nov THERMODYNAMICS (Com. to ME, AE, AME) Time: 3 hours Max.
SET - 1 1. a) Discuss about PMM I and PMM II b) Explain about Quasi static process. c) Show that the COP of a heat pump is greater than the COP of a refrigerator by unity. d) What is steam quality? What
More informationDesign of Prototype Supercritical CO2 Superheater Heat Exchanger
The 6th International Supercritical CO2 Power Cycles Symposium March 27-29, 2018, Pittsburgh, Pennsylvania Design of Prototype Supercritical CO2 Superheater Heat Exchanger Han Seo Postdoctoral Researcher
More informationCHAPTER 5 MASS AND ENERGY ANALYSIS OF CONTROL VOLUMES
Thermodynamics: An Engineering Approach 8th Edition in SI Units Yunus A. Ç engel, Michael A. Boles McGraw-Hill, 2015 CHAPTER 5 MASS AND ENERGY ANALYSIS OF CONTROL VOLUMES Objectives Develop the conservation
More informationS-CO 2 Brayton Loop Transient Modeling
The 4 th International Symposium Supercritical CO 2 Power Cycles Technologies for Transformational Energy Conversion September 9-10, 2014, Pittsburgh, Pennsylvania S-CO 2 Brayton Loop Transient Modeling
More informationProblems in chapter 9 CB Thermodynamics
Problems in chapter 9 CB Thermodynamics 9-82 Air is used as the working fluid in a simple ideal Brayton cycle that has a pressure ratio of 12, a compressor inlet temperature of 300 K, and a turbine inlet
More informationThe 5th International Symposium - Supercritical CO 2 Power Cycles March 28-31, 2016, San Antonio, Texas
The 5th International Symposium - Supercritical CO 2 Power Cycles March 28-31, 2016, San Antonio, Texas 4 Wnet=82 kw (ηgenerator=95%) Flue gas 1.94 kg/s T=650 C P=13,500 kpa Turbine A P=13,500 kpa Turbine
More informationA Scroll Expander with Heating Structure and Their Systems
Purdue University Purdue e-pubs International Engineering Conference School of Mechanical Engineering 4 A Expander with Heating Structure and Their Systems Young Min Kim Korea Institute of Machinery &
More informationUNIVERSITY OF TORONTO FACULTY OF APPLIED SCIENCE AND ENGINEERING FINAL EXAMINATION, DECEMBER 2008 MIE 411H1 F - THERMAL ENERGY CONVERSION
UNIVERSITY OF TORONTO FACULTY OF APPLIED SCIENCE AND ENGINEERING FINAL EXAMINATION, DECEMBER 2008 MIE 411H1 F - THERMAL ENERGY CONVERSION Exam Type: X Examiner: J.S. Wallace You may use your copy of the
More informationMECHANICAL ENGINEERING DEPARTMENT, OITM
Sem.:4 th Subject: Energy Conversion Paper: ME-201E UNIT-1 Q1. Explain the seismometer with its working principle. (Important Question) (20) Q2. Classify the fuels and define calorific value of fuels.
More informationDynamic modeling and transient analysis of a molten salt heated recompression supercritical CO 2 Brayton cycle
Dynamic modeling and transient analysis of a molten salt heated recompression supercritical CO 2 Brayton cycle For the 6 th International Supercritical CO 2 Power Cycles Symposium Jinyi ZHANG EDF R&D China
More informationT.E. (Mech., Mech. S/W) (Semester II) Examination, 2011 TURBOMACHINES (New) (2008 Pattern)
*4063218* [4063] 218 T.E. (Mech., Mech. S/W) (Semester II) Examination, 2011 TURBOMACHINES (New) (2008 Pattern) Time : 3 Hours Marks : 100 Instructions : 1) Answer any three questions from each Section.
More informationOUTCOME 2 TUTORIAL 2 STEADY FLOW PLANT
UNIT 47: Engineering Plant Technology Unit code: F/601/1433 QCF level: 5 Credit value: 15 OUTCOME 2 TUTORIAL 2 STEADY FLOW PLANT 2 Be able to apply the steady flow energy equation (SFEE) to plant and equipment
More informationSupercritical CO2 Brayton Cycles and Their Application as a Bottoming Cycle. Grant Kimzey UTSR Intern Project Summary Webcast September 7, 2012
Supercritical CO2 Brayton Cycles and Their Application as a Bottoming Cycle Grant Kimzey UTSR Intern Project Summary Webcast September 7, 2012 Contents Introduction Assumptions and Design Parameters Benchmarks
More informationThermoelectric Design
INTERAMERICAN UNIVERSITY OF BAYAMON PUERTO RICO Thermoelectric Design Thermodynamic 2 Erik T. Rosado Rolando Santiago 5/15/2012 TABLE OF CONTENTS TABLE OF FIGURE... 2 TABLE OF DATA RESULTS... 2 ABSTRACT...
More informationSecond Law Analysis of a Carbon Dioxide Transcritical Power System in Low-grade Heat Source Recovery
Second Law Analysis of a Carbon Dioxide Transcritical Power System in Low-grade Heat Source Recovery Y. Chen, Almaz Bitew Workie, Per Lundqvist Div. of Applied Thermodynamics and Refrigeration, Department
More informationS-CO 2 Brayton Loop Transient Modeling
S-CO 2 Brayton Loop Transient Modeling The 4 th International Symposium on Supercritical CO 2 Power Cycles September 9 & 10, 2014 Background Outline Model Results and Comparisons with Test Data Steady
More informationStationary Combustion Systems Chapter 6
Stationary Combustion Systems Chapter 6 Stationary combustion systems presently supply most of the earth s electricity. Conversion will take time, so study of these systems in order to improve them is
More informationExperimental Investigation of a Hermetic Scroll Expander-Generator
Purdue University Purdue e-pubs International Compressor Engineering Conference School of Mechanical Engineering 1994 Experimental Investigation of a Hermetic Scroll Expander-Generator R. Zanelli Swiss
More information"Leveraging Cross-Industry Know-How for Thermodynamic Cycles & Turbomachinery Component Innovation"
"Leveraging Cross-Industry Know-How for Thermodynamic Cycles & Turbomachinery Component Innovation" Wednesday, June 17, 2015 Stage Presentation ASME TURBOEXPO 2015 1 About SoftInWay Founded in 1999, we
More informationApplication of an Integrally Geared Compander to an sco 2 Recompression Brayton Cycle
Application of an Integrally Geared Compander to an sco 2 Recompression Brayton Cycle Dr. Jason Wilkes Dr. Tim Allison Jeffrey Bennett Joshua Schmitt Dr. Karl Wygant Rob Pelton Werner Bosen An integrally
More informationa. The power required to drive the compressor; b. The inlet and output pipe cross-sectional area. [Ans: kw, m 2 ] [3.34, R. K.
CHAPTER 2 - FIRST LAW OF THERMODYNAMICS 1. At the inlet to a certain nozzle the enthalpy of fluid passing is 2800 kj/kg, and the velocity is 50 m/s. At the discharge end the enthalpy is 2600 kj/kg. The
More information- 2 - SME Q1. (a) Briefly explain how the following methods used in a gas-turbine power plant increase the thermal efficiency:
- 2 - Q1. (a) Briefly explain how the following methods used in a gas-turbine power plant increase the thermal efficiency: i) regenerator ii) intercooling between compressors (6 marks) (b) Air enters a
More informationCHAPTER 1 BASIC CONCEPTS
GTU Paper Analysis CHAPTER 1 BASIC CONCEPTS Sr. No. Questions Jan 15 Jun 15 Dec 15 May 16 Jan 17 Jun 17 Nov 17 May 18 Differentiate between the followings; 1) Intensive properties and extensive properties,
More informationANALYSIS AND OPTIMIZATION FOR OFF-DESIGN PERFORMANCE OF THE RECOMPRESSION sco2 CYCLES FOR HIGH TEMPERATURE CSP APPLICATIONS
The 5 th International Symposium Supercritical CO2 Power Cycles March 29 31, 2016, San Antonio, Texas ANALYSIS AND OPTIMIZATION FOR OFF-DESIGN PERFORMANCE OF THE RECOMPRESSION sco2 CYCLES FOR HIGH TEMPERATURE
More informationMULTI-OBJECTIVE OPTIMIZATION ON SUPERCRITICAL CO 2 RECOMPRESSION BRAYTON CYCLE USING KRIGING SURROGATE MODEL
Sun, L., et al.: Multi-Objective Optimization on Supercritical CO Recompression... S309 MULTI-OBJECTIVE OPTIMIZATION ON SUPERCRITICAL CO RECOMPRESSION BRAYTON CYCLE USING KRIGING SURROGATE MODEL by Lei
More informationMCG THERMODYNAMICS II. 22 April 2008 Page 1 of 7 Prof. W. Hallett
Faculté de génie Génie mécanique Faculty of Engineering Mechanical Engineering MCG2131 - THERMODYNAMICS II 22 April 2008 Page 1 of 7 Prof. W. Hallett Closed book. Non-programmable calculators only allowed.
More informationThermal Design Optimization of Finned Shell and Tube Heat Exchanger Using Taguchi Approach
Journal of Emerging Trends in Engineering and Applied Sciences (JETEAS) 8(3):131-135 (ISSN: 2141-7016) Scholarlink Research Institute Journals, 2017 (ISSN: 2141-7016) jeteas.scholarlinkresearch.com Thermal
More informationDesign Optimisation of the Graz Cycle Prototype Plant
Institute for Thermal Turbomaschinery and Machine Dynamics Graz University of Technology Erzherzog-Johann-University Design Optimisation of the Graz Cycle Prototype Plant Presentation at the ASME Turbo
More informationAN EXPERIENCE IN THERMODYNAMIC TEST OF LOW HEAD TURBINE IN THAILAND THE CASE OF MAE NGAT HYDRO POWER PLANT
AN EXPERIENCE IN THERMODYNAMIC TEST OF LOW HEAD TURBINE IN THAILAND THE CASE OF MAE NGAT HYDRO POWER PLANT Matha Tantaworranart Performance Test Engineer at Hydro Power Plant Performance Test Section,
More informationDevelopment of A Transient Analysis Code for S-CO2 Power Conversion System
The 6th International Supercritical CO2 Power Cycles Symposium March 27-29, 2018, Pittsburgh, Pennsylvania Development of A Transient Analysis Code for S-CO2 Power Conversion System Chuntian Gao Phd Xi
More informationCHAPTER 1 BASIC CONCEPTS THEORY
CHAPTER 1 BASIC CONCEPTS THEORY 1. Explain briefly the following terms with diagram (wherever necessary): a) Thermodynamic System, Surroundings & Boundary b) Control Volume & Control Surface c) Intensive
More informationChapter 1 STEAM CYCLES
Chapter 1 STEAM CYCLES Assoc. Prof. Dr. Mazlan Abdul Wahid Faculty of Mechanical Engineering Universiti Teknologi Malaysia www.fkm.utm.my/~mazlan 1 Chapter 1 STEAM CYCLES 1 Chapter Objectives To carry
More informationASSIGNMENT 2 Coal and Ash Handling System and Draught Systems
ASSIGNMENT 1 Thermal Power Plant & High Pressure Boiler 1. State the factors to be considered for selection of site for thermal power plant 2. State desirable to control the super heat temperature. Explain
More informationDesign and Performance Characterization of a Micro-pin-fin sco 2 Recuperator
Design and Performance Characterization of a Micro-pin-fin sco 2 Recuperator Cameron Naderi, Graduate Student Erfan Rasouli, Post Doctoral Scholar Vinod Narayanan*, Professor sco 2 Symposium, Pittsburg
More informationEng Thermodynamics I: Sample Final Exam Questions 1
Eng3901 - Thermodynamics I: Sample Final Exam Questions 1 The final exam in Eng3901 - Thermodynamics I consists of four questions: (1) 1st Law analysis of a steam power cycle, or a vapour compression refrigeration
More informationChapter 1 Basic Concepts
Jan 15 Jun 15 Chapter 1 Basic Concepts GTU Paper Analysis (New Syllabus) Sr. No. Questions Differentiate between the followings; 1) Intensive properties and extensive properties, 2) Point function and
More informationThermodynamics: An Engineering Approach, 6 th Edition Yunus A. Cengel, Michael A. Boles McGraw-Hill, 2008
Thermodynamics: An Engineering Approach, 6 th Edition Yunus A. Cengel, Michael A. Boles McGraw-Hill, 2008 Chapter 5 MASS AND ENERGY ANALYSIS OF CONTROL VOLUMES SUMMARY 1 CONSERVATION OF MASS Conservation
More informationTransient Modeling of a Supercritical CO 2 Power Cycle in GT-SUITE and Comparison with Test Data. Echogen Power Systems 1
Transient Modeling of a Supercritical CO 2 Power Cycle in GT-SUITE and Comparison with Test Data Dr. Vamshi K. Avadhanula Systems Engineer Dr. Timothy J. Held Chief Technology Officer 1 Synopsis for today
More informationR13. (12M) efficiency.
SET - 1 II B. Tech I Semester Regular/Supplementary Examinations, Oct/Nov - 2016 THERMAL AND HYDRO PRIME MOVERS (Electrical and Electronics Engineering) Time: 3 hours Max. Marks: 70 Note: 1. Question Paper
More informationLiquid-Flooded Ericsson Power Cycle
Purdue University Purdue e-pubs International Compressor Engineering Conference School of Mechanical Engineering 2014 Liquid-Flooded Ericsson Power Cycle Nelson A. James Purdue University, United States
More informationLecture No.3. The Ideal Reheat Rankine Cycle
Lecture No.3 The Ideal Reheat Rankine Cycle 3.1 Introduction We noted in the last section that increasing the boiler pressure increases the thermal efficiency of the Rankine cycle, but it also increases
More informationPower cycle development
Power cycle development Steam cycles dominant for >300 yrs, mostly Rankine Gas Brayton cycles catching up last 50 years Organic Rankine Cycles (ORC) relatively recent 2 Why a new power cycle? Steam Good
More informationR13 SET - 1 '' ''' '' ' '''' Code No: RT31035
R13 SET - 1 III B. Tech I Semester Regular/Supplementary Examinations, October/November - 2016 THERMAL ENGINEERING II (Mechanical Engineering) Time: 3 hours Max. Marks: 70 Note: 1. Question Paper consists
More information[4163] T.E. (Mechanical) TURBO MACHINES (2008 Pattern) (Common to Mech. S/W) (Sem. - II)
Total No. of Questions : 12] P1061 SEAT No. : [Total No. of Pages : 7 [4163] - 218 T.E. (Mechanical) TURBO MACHINES (2008 Pattern) (Common to Mech. S/W) (Sem. - II) Time : 3 Hours] [Max. Marks :100 Instructions
More informationCOMPARATIVE ANALYSES OF TWO IMPROVED CO 2 COMBINED COOLING, HEATING, AND POWER SYSTEMS DRIVEN BY SOLAR ENERGY
S93 Introduction COMPARATIVE ANALYSES OF TWO IMPROVED CO 2 COMBINED COOLING, HEATING, AND POWER SYSTEMS DRIVEN BY SOLAR ENERGY by Wanjin BAI a* and Xiaoxiao XU b a School of Mechanical and Vehicle Engineering,
More informationDesign of radial turbomachinery for supercritical CO 2 systems using theoretical and numerical CFD methodologies
Available online at www.sciencedirect.com ScienceDirect Energy Procedia 123 (2017) 313 320 www.elsevier.com/locate/procedia 1st International Conference on Sustainable Energy and Resource Use in Food Chains,
More informationPOWER RECOVERY IN FLOATING LNG REGASIFICATION PLANTS
POWER RECOVERY IN FLOATING LNG REGASIFICATION PLANTS Arindom Goswami Senior Principal Engineer M. W. Kellogg Ltd Greenford, UB6 0JA, U.K. arindom.goswami@mwkl.co.uk Hans E. Kimmel Executive Director R&D
More informationPerformance of a Gas Turbine Power Plant
International Journal of Mechanical Engineering and Applications 2017; 5(1): 60-69 http://www.sciencepublishinggroup.com/j/ijmea doi: 10.11648/j.ijmea.20170501.18 ISSN: 2330-023X (Print); ISSN: 2330-0248
More informationAndy Schroder Mark Turner University of Cincinnati, Cincinnati, OH, 45221, U.S.A. Abstract
Mapping the Design Space of a Recuperated, Recompression, Precompression Supercritical Carbon Dioxide Power Cycle with Intercooling, Improved Regeneration, and Reheat Andy Schroder Mark Turner University
More information1. INTRODUCTION. Corresponding author. Received December 18, 2008 Accepted for Publication April 9, 2009
DEVELOPMENT OF A SIMPLIFIED MODEL FOR ANALYZING THE PERFORMANCE OF KALIMER-600 COUPLED WITH A SUPERCRITICAL CARBON DIOXIDE BRAYTON ENERGY CONVERSION CYCLE SEUNG-HWAN SEONG *, TAE-HO LEE and SEONG-O KIM
More informationLecture No.1. Vapour Power Cycles
Lecture No.1 1.1 INTRODUCTION Thermodynamic cycles can be primarily classified based on their utility such as for power generation, refrigeration etc. Based on this thermodynamic cycles can be categorized
More informationOPTIMIZATION OF PARAMETERS FOR HEAT RECOVERY STEAM GENERATOR (HRSG) IN COMBINED CYCLE PLANTS
OPTIMIZATION OF PARAMETERS FOR HEAT RECOVERY STEAM GENERATOR (HRSG) IN COMBINED CYCLE PLANTS Muammer Alus, Milan V. Petrovic University of Belgrade-Faculty of Mechanical Engineering, Laboratory of Thermal
More informationChapter 5 MASS AND ENERGY ANALYSIS OF CONTROL VOLUMES
Thermodynamics: An Engineering Approach Seventh Edition Yunus A. Cengel, Michael A. Boles McGraw-Hill, 2011 Chapter 5 MASS AND ENERGY ANALYSIS OF CONTROL VOLUMES Copyright The McGraw-Hill Companies, Inc.
More informationCode No: RR Set No. 1
Code No: RR310303 Set No. 1 III B.Tech I Semester Regular Examinations, November 2006 THERMAL ENGINEERING-II (Mechanical Engineering) Time: 3 hours Max Marks: 80 Answer any FIVE Questions All Questions
More informationDesign considerations on a small scale supercritical CO 2 power system for industrial high temperature waste heat to power recovery applications
on Supercritical CO 2 (sco 2 ) Power Systems Design considerations on a small scale supercritical CO 2 power system for industrial high temperature waste heat to power recovery applications, S. A. Tassou,
More informationPRACTICAL ASPECTS OF SUPERCRITICAL CARBON DIOXIDE BRAYTON SYSTEM TESTING
The 4th International Symposium - Supercritical CO2 Power Cycles September 9-10, 2014, Pittsburgh, Pennsylvania PRACTICAL ASPECTS OF SUPERCRITICAL CARBON DIOXIDE BRAYTON SYSTEM TESTING E. M. Clementoni
More informationComparative Efficiency of Geothermal Vapor-Turbine Cycles
Proceedings World Geothermal Congress 2005 ntalya, Turkey, 24-29 pril 2005 Comparative Efficiency of Geothermal Vapor-Turbine Cycles M. Boyarskiy, O. Povarov,. Nikolskiy,. Shipkov NUK Stock Company, 9.Krasnokazarmennaya
More informationSeawater Utilization Plant Research Center, Korea Research Institute of Ships & Ocean Engineering
2015. 09.02 Seawater Utilization Plant Research Center, Korea Research Institute of Ships & Ocean Engineering Seung-Teak Lim, Ho-Saeng Lee, Hyeon-ju Kim Introduction Organic Rankine Cycle Basic cycle of
More informationSUPERCRITICAL CO 2 POWER CYCLE DEVELOPMENT SUMMARY AT SANDIA NATIONAL LABORATORIES
SUPERCRITICAL CO 2 POWER CYCLE DEVELOPMENT SUMMARY AT SANDIA NATIONAL LABORATORIES Steven A. Wright*, Thomas M. Conboy, and Gary E. Rochau International Conference on ORC Power Systems Delft University
More informationWhite Rose Research Online URL for this paper: Version: Accepted Version
This is a repository copy of Thermodynamic analysis and preliminary design of closed Brayton cycle using nitrogen as working fluid and coupled to small modular Sodium-cooled fast reactor (SM-SFR). White
More informationLECTURE-14. Air Refrigeration Cycles. Coefficient of Performance of a Refrigerator:
Lecturer: -Dr. Esam Mejbil Abid Subject: Air Conditioning and Refrigeration Year: Fourth B.Sc. Babylon University College of Engineering Department of Mechanical Engineering LECTURE-14 Air Refrigeration
More informationPerformance Benefits for Organic Rankine Cycles with Flooded Expansion
Purdue University Purdue e-pubs Publications of the Ray W. Herrick Laboratories School of Mechanical Engineering 6-2-2010 Performance Benefits for Organic Rankine Cycles with Flooded Expansion Brandon
More informationwb Thermodynamics 2 Lecture 10 Energy Conversion Systems
wb1224 - Thermodynamics 2 Lecture 10 Energy Conversion Systems Piero Colonna, Lecturer Prepared with the help of Teus van der Stelt 13-12-2010 Delft University of Technology Challenge the future Content
More informationAnalysis of a Directly Heated Oxyfuel Supercritical Power Generation System
AIAA SciTech 4-8 January 2016, San Diego, California, USA 54th AIAA Aerospace Sciences Meeting AIAA 2016-0991 Analysis of a Directly Heated Oxyfuel Supercritical Power Generation System A S M Arifur Chowdhury
More informationAREN 2110: Thermodynamics Spring 2010 Homework 7: Due Friday, March 12, 6 PM
AREN 2110: Thermodynamics Spring 2010 Homework 7: Due Friday, March 12, 6 PM 1. Answer the following by circling the BEST answer. 1) The boundary work associated with a constant volume process is always
More informationGAS COOLING HEAT TRANSFER AND PRESSURE DROP CHARATERICTICS OF CO 2 /OIL MIXTURE IN A MICROCHANNEL ABSTRACT
GAS COOLING HEAT TRANSFER AND PRESSURE DROP CHARATERICTICS OF CO /OIL MIXTURE IN A MICROCHANNEL R. YUN, Y. HWANG*, AND R. RADERMACHER Center for Environmental Energy Engineering, Department of Mechanical
More informationChapters 5, 6, and 7. Use T 0 = 20 C and p 0 = 100 kpa and constant specific heats unless otherwise noted. Note also that 1 bar = 100 kpa.
Chapters 5, 6, and 7 Use T 0 = 20 C and p 0 = 100 kpa and constant specific heats unless otherwise noted. Note also that 1 bar = 100 kpa. 5-1. Steam enters a steady-flow device at 16 MPa and 560 C with
More informationChapter 5 MASS AND ENERGY ANALYSIS OF CONTROL VOLUMES
Thermodynamics: An Engineering Approach Seventh Edition in SI Units Yunus A. Cengel, Michael A. Boles McGraw-Hill, 2011 Chapter 5 MASS AND ENERGY ANALYSIS OF CONTROL VOLUMES Copyright The McGraw-Hill Companies,
More informationThermodynamic Simulation of Steam Power Cycles using GUI- MatLab Interfaces
RESEARCH ARTICLE OPEN ACCESS Thermodynamic Simulation of Steam Power Cycles using GUI- MatLab Interfaces Pedro F. Arce, Nian F. Vieira Chemical Engineering Department, School Engineering of Lorena, University
More informationSIMULATION AND PERFORMANCE ANALYSIS OF THE NEW GEOTHERMAL CO-GENERATION POWER PLANT (OV-5) AT SVARTSENGI
SIMULATION AND PERFORMANCE ANALYSIS OF THE NEW GEOTHERMAL CO-GENERATION POWER PLANT (OV-5) AT SVARTSENGI Masoud Soltani-Hosseini 1, Hallgrimur G. Sigurdsson 2 and Geir Thorolfsson 3 1 Niroo Research Institute,
More informationME ENGINEERING THERMODYNAMICS UNIT III QUESTION BANK SVCET
1. A vessel of volume 0.04m 3 contains a mixture of saturated water and steam at a temperature of 250 0 C. The mass of the liquid present is 9 kg. Find the pressure, mass, specific volume, enthalpy, entropy
More informationModelling and Experimental Investigations of ORC Systems
Modelling and Experimental Investigations of ORC Systems Y.T. Ge, L. Li, X. Luo, S.A. Tassou, Brunel University London, Uxbridge, Middlesex, UB83PH, UK Outline of Presentation Test rigs of CO 2 transcritical
More informationPotential of Allam cycle with natural gas to reduce carbon dioxide emission in India
The 6 th International Symposium-Supercritical CO2 Power Cycles, March 27-29, 2018, Pittsburgh, PA Potential of Allam cycle with natural gas to reduce carbon dioxide emission in India Amit Mulchand Nabros
More informationDEVELOPMENT OF A SUPERCRITICAL CO2 BRAYTON ENERGY CONVERSION SYSTEM COUPLED WITH A SODIUM COOLED FAST REACTOR
DEVELOPMENT OF A SUPERCRITICAL CO2 BRAYTON ENERGY CONVERSION SYSTEM COUPLED WITH A SODIUM COOLED FAST REACTOR JAE-EUN CHA *, TAE-HO LEE, JAE-HYUK EOH, SUNG-HWAN SEONG, SEONG-O KIM, DONG-EOK KIM, MOO- HWAN
More informationChapter 10 Vapor and Combined Power Cycles
Chapter 10 Vapor and Combined Power Cycles Dr. Mohammad Tarawneh Thermodynamics: An Engineering Approach, 5th edition by Yunus A. Çengel and Michael A. Boles We consider power cycles where the working
More informationA Further Step Towards a Graz Cycle Power Plant for CO 2 Capture
Institute for Thermal Turbomaschinery and Machine Dynamics Graz University of Technology Erzherzog-Johann-University A Further Step Towards a Graz Cycle Power Plant for CO 2 Capture Presentation at the
More informationChapter 10. In Chap. 9 we discussed gas power cycles for which the VAPOR AND COMBINED POWER CYCLES. Objectives
Chapter 0 VAPOR AND COMBINED POWER CYCLES In Chap. 9 we discussed gas power cycles for which the working fluid remains a gas throughout the entire cycle. In this chapter, we consider vapor power cycles
More informationSeptember 10, Megan Huang* & Dr. Chandrashekhar Sonwane
THERMODYNAMICS OF CONVENTIONAL AND NON- CONVENTIONAL SCO 2 RECOMPRESSION BRAYTON CYCLES WITH DIRECT AND INDIRECT HEATING September 10, 2014 Megan Huang* & Dr. Chandrashekhar Sonwane Agenda Efficiency of
More informationChapter 10 VAPOR AND COMBINED POWER CYCLES
Thermodynamics: An Engineering Approach, 6 th Edition Yunus A. Cengel, Michael A. Boles McGraw-Hill, 2008 Chapter 10 VAPOR AND COMBINED POWER CYCLES Copyright The McGraw-Hill Companies, Inc. Permission
More information