/ / 1 Einstein Fig. 1 The principle diagram of Einstein refrigeration cycle system 2 Einstein 2. 1 Ⅰ Einstein 10 2 / / 2 I Einstein 10 Fig. 2 T

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1 JOURNAL OF ENGINEERING FOR THERMAL ENERGY AND POWER Vol. 31 No. 10 OctAu 殏檪殏殏檪檪檪檪檪檪檪檪檪檪檪檪檪殏 Einstein Einstein Einstein 3 Einstein I II III 3 Einstein II COP COP 5 Einstein Einstein 6 TK A DOI /j. cnki. rndlgc COP Einstein COP 1927 Von Georg Einstein Szilard Einstein Delano Einstein White 7 Mejbri / 3 COP 2 Einstein 1 Einstein 3 Einstein 9 1 / 4 / ZZ

2 / / 1 Einstein Fig. 1 The principle diagram of Einstein refrigeration cycle system 2 Einstein 2. 1 Ⅰ Einstein 10 2 / / 2 I Einstein 10 Fig. 2 The principle diagram of Einstein refrigeration system improved by Wang Rujin 10

3 10 Einstein Ⅱ Einstein / 11 3 Ⅰ / Ⅰ Ⅰ / / 4 III Einstein 12 Fig. 4 The principle diagram of Einstein refrigeration system improved by Chen Yongjun 12 3 II Einstein 11 Fig. 3 The principle diagram of Einstein refrigeration system improved by Ye Peng III MPa T e 283 K 12 T a 318 K T c 303 K T g K kw 13 m v = m 1 1

4 Tab. 1 Initial parameters of the cycle simulation Einstein Engineering Equation Solver I II III P /MPa 0. 4 P /MPa 0. 4 P /MPa 0. 4 T e T 3 / 10 T e T 3 / 10 T e T 9 / 10 T c / 30 T c T 2 / 30 T c T 11 / 30 T a / 45 T a T 1 T 7 / 45 T a T 10 T 8 / 45 4 T g / 100 T g T b T 10 / 100 T g T b / 100 T 3-2 / 7 T 5-3 / 7 T 9-7 / T 3-4 / 12 T 5-4 / 12 T 9-11 / 7 T / 7 T r T 9 T 16 / 30 T 1-5 / 12 3 ~ 5 n 1 /mol s T 7-11 / 12 T 3-4 / Einstein Tab. 2 Thermodynamic models of three improved Einstein Refrigeration Cycles I II III x a 2 m 2 + m 4 = y a 3 m 3 m 3 + m 4 = m 5 m 11 + m 7 = m 9 x b 2 m 2 + m 4 = y b 3 m 3 x a 3 m 3 + x a 4 m 4 = y a 5 m 5 m 11 x b 11 + m 7 x b 7 = m 9 y b 9 / m 2 h 2 + m 4 h 4 + Q evap = m 3 h 3 m 1 + m 11 = m 10 + m 6 + m 13 x a 10 m 10 + x a 6 m 6 + x a 13 m 13 = y a 1 m 1 + y a 11 m 11 m 10 h 10 + m 6 h 6 + m 13 h 13 = m 1 h 1 + m 11 h 11 + Q cond m 7 = m 5 + m 9 + m 13 m 3 h 3 + m 4 h 4 + Q evap = m 5 h 5 m 1 = m 2 m 1 x b 1 = m 2 y b 2 m 1 h 1 = m 2 h 2 + Q cond m 1 + m 7 = m 6 + m 11 x a 11 m 11 + x a 6 m 6 = y a 1 m 1 + y a 7 m 7 m 6 x b 6 = m 1 y b 1 m 6 h 6 + m 11 h 11 = m 1 h 1 + m 7 h 7 + Q abs m 8 + m 15 = m 12 + m 13 + m 14 m 11 h 11 + m 7 h 7 + Q evap = m 9 h 9 m 8 = m 11 m 8 x b 8 = m 11 y b 11 m 8 h 8 = Q cond + m 11 h 11 m 10 + m 8 = m 6 + m 9 x b 9 m 9 + x b 6 m 6 = y b 8 m 8 + y b 10 m 10 m 6 h 6 + m 9 h 9 = m 10 h 10 + m 8 h 8 + Q abs x a 7 m 7 = y a 5 m 5 + y a 13 m 13 + y a 9 x a 8 m 8 + x a 15 m 15 = y a 12 m 12 + y a 13 / m 9 m 13 + y a 14 m 14 / m 5 h 5 + m 9 h 9 + m 13 h 13 = m 7 h 7 m 12 h 12 + m 13 h 13 + m 14 h 14 = m 8 m 1 = m 3 + m 5 x a 1 m 1 = y a 3 m 3 + y a 5 m 5 m 3 h 3 + m 5 h 5 = m 1 h 1 + Q gen + Q gen + Q bp m 10 = m 14 m 12 = m 5 x a 12 = y a 5 x a 10 = y a 14 m 10 h 10 + m 12 h 12 = m 5 h 5 + m 14 h 14 m 10 = m 9 m 11 = m 7 x a 11 = y a 7 x a 9 = y a 10 m 9 h 9 + m 11 h 11 = m 10 h 10 + m 7 h 7 m 5 = m 4 m 3 = m 6 m 1 = m 2 m 3 h 3 + m 1 h 1 + m 4 h 5 = m 3 h 6 + m 1 h 2 + m 4 h 4 h 8 + m 15 h 15 + Q gen + Q bp m 14 = m 16 + m 9 x a 14 m 14 = y a 16 m 16 + y a 9 m 9 m 14 h 14 = m 16 h 16 + m 9 h 9 + Q acr m 11 = m 13 m 8 = m 7 x a 7 = y a 8 x a 13 = y a 11 m 13 h 13 + m 7 h 7 = m 11 h 11 + m 8 h 8 m 4 = m 16 m 3 = m 2 m 5 = m 6 x b 2 = x b 3 y a 5 = y a 6 m 9 h 16 + m 5 h 5 + m 2 h 2 = m 3 h 3 + m 6 h 6 + m 4 h 4 m 3 = m 4 x a 3 m 3 = y a 4 m 4 m 3 h 3 = m 4 h 4 + Q acr1 m 5 = m 6 m 1 = m 10 m 5 x a 5 = m 6 y a 6 m 5 h 5 = m 6 h 6 + Q acr2 m 1 h 1 = m 10 h 10 + Q acr3 m mol /l Q / W x y a b x a i y a i i

5 10 Einstein 5 3 I Tab. 3 Thermodynamic parameters of each state point in system I NH 3 C 4 H 10 H 2 O /K /J g - 1 /g s Q g = W Q c = W Q acr = W Q e = W Q bp = W COP = Q e / Q g + Q bp = II Tab. 4 Thermodynamic parameters of each state point in system II NH 3 C 4 H 10 H 2 O /K /J g - 1 /g s Q g = W Q c = W Q a = W Q acr = W Q e = W Q bp = W COP = Q e / Q g + Q bp = COP 285 K 3 COP COP MPa K II COP COP COP 278 ~ COP K 3 COP II COP /

6 COP 5 COP 5 III Tab. 5 Thermodynamic parameters of each state point in system III NH 3 C 4 H 10 H 2 O /K /J g - 1 /g s Q g = W Q c = W Q a = W Q acr = W Q e = W COP = Q e /Q g = K I III COP COP COP 298 K COP COP Fig. 5 COP variation with respect to evaporation temperature COP 6 COP 298 ~ 308 K 3 COP I COP I 6 COP 303 K I II COP Fig. 6 COP variation with respect to condensing temperature

7 10 Einstein COP COP I 7 II COP III I II COP COP 3 III K COP ~ 288 K 3 COP 7 COP 5 Fig. 7 COP variation with respect to generation COP temperature K COP 5 Einstein 3 Einstein Einstein 3 COP COP MPa 283 1VON PBC GEORG MC. RefrigeratorP. US US K 318 K 303 K 373 K 1 kw 3 COP II COP 2 I II / K 3 COP ~ 308 K 3 COP I 303 K I II COP K I COP EINSTEIN A SZILARD L. Refrigeration P. United States J XUE Xiang-mei LIU Dao-pingWANG Ru-jin. Research progress of single pressure absorption refrigeration technology J. Refrigera-

8 櫋櫋櫋櫋櫋櫋櫋櫋櫋櫋櫋櫋櫋櫋櫋 tion and Air-conditioning J J DAI Yong-qing GENG Hui-bin CAI Xiao-rong. Review and prospects of lithium bromide absorption refrigeration technology J. 4. WANG Ru-jin LIU Dao-ping XUE Xiang-mei. Design of the single pressure absorption refrigerator with einstein cycle J. Machinery Design & Manufacture Einstein D.. Refrigeration Technology SONG Mei-feng LIU Dao-ping HUANG Wen-jian. Development of single pressure absorption-type refrigeration technology J. Journal of HV&AV DELANO A. Design analysis of the einstein refrigeration cycle D. Atlanta Georgia Institute of Technology WHITE S J. Bubble pump design and performance J. Aldaco MEJBRI K EZZINE N B GUIZANI Y et al. Discussion of the feasibility of the einstein refrigeration cycle J. International Journal of Refrigeration J. YE Peng. Design study on refrigerator of Einstein refrigeration cycle D. Shanghai University of Shanghai for Science and Technology D CHEN Yong-jun. Redesign analysis of single pressure absorption system on Einstein refrigeration cycle D. Shanghai University of Shanghai for Science and Technology Einstein J YE Peng LIU Dao-ping LIANG Yu. Feasibility analysis on einstein refrigeration cycle capable of using low qualified heat source 9EINSTEIN A SZILARD L. RefrigerationP. United States Einstein J 殹櫋殹殹殹 M501 Gas Turbine World 2014 ~ 2015 Mitsubishi Hitachi Power Systems 60 Hz M mm 60 Hz M501 /kw /kj kwh - 1 /% /kw /kw 1 1 M501DA M501F M501G M501GAC M501J M501JAC >

9 Einstein = Operational Feasibility Analysis of the Improved Einstein Refrigeration Cycle System LIN Fa-long LIU Dao-ping AN Li-huan YANG Meng Institute of Refrigeration Technology University of Shanghai for Science and Technology Shanghai China Post code / / Journal of Engineering for Thermal Energy & Power ~ 8 In the paper the principle of single pressure absorption-type Einstein refrigeration cycle was introduced. Three improved Einstein refrigeration systems I II III built in our previous work were compared. The thermodynamic models of the three systems were established using mass and energy conservation law. Then their performances were analyzed. The results show that system II has the highest COP under the same working conditions. Changing the working conditions cannot very effectively improve the system COP. But the system refrigeration performance can be effectively improved by reasonably matching system components optimizing pipeline resistance using heat recovery system and efficient bubble pump and then choosing the best generation temperature. This study is expected to provide important guidance for Einstein refrigeration cycle system performance optimization and industrial applications. Key words Einstein cycle single pressure absorption-type refrigeration improvement feasibility analysis = Mixed Vapor Condensation Outside Horizontal Tube under Different Vapor Velocities QIAO Hong-binWANG ShunHU Shen-hua Electric Power Simulation and Control Engineering Center Nanjing Institute of Technology Nanjing China Post Code / / Journal of Engineering for Thermal Energy & Power ~ 14 Reported herein are the experimental data for so-called Marangoni condensation of steam ethanol outside the horizontal tube surfaces at vapor pressure of 70 kpa. In order to determine the effect of vapor velocity on Marangoni condensation heat flux and vapor-to-surface temperature differences were measured for steam-ethanol mixture over a wide range of composition at vapor velocity of m /s m /sand m /s. The experimental results show that for pure steam the steam velocity has a great effect on the condensation heat transfer characteristics. For ethanol-water mixture steam heat transfer coefficient increases with steam velocity and the increase magnitude is associated with alcohol concentration. Specifically in the lower concentration range 1% 2% the heat transfer coefficient increases with steam velocity and the increase amplitude reaches maximum at 2% concentration. In the higher concentration range 5% 10% and 20% the increase amplitude of the heat transfer coefficient reduces as steam velocity increases. Key words horizontal tube vapor velocity steam-ethanol mixture vapor Marangoni condensation = Performance Optimization for Cascaded Diversion ORC System LI Wei-kangYANG Xin-LeHUANG Fei-feiDAI Wen-zhi School of Mechanical Engineering Liaoning Technical University Fuxin Liaoning China Post Code / / Journal of Engineering for Thermal Energy & Power ~ 19 In this paper a cascade diversion ORC system was proposed and the thermodynamic models with or without diversion were built. The genetic algorithm was used to optimize the performance where the system took the evaporation

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untitled 20 1 2010 10 Vol.20 Special 1 The Chinese Journal of Nonferrous Metals Oct. 2010 1004-0609(2010)S1-s0127-05 Ti-6Al-4V 1 2 2 (1. 710016 2., 710049) 500~1 000 20 Ti-6Al-4V(TC4) TC4 800 TC4 800 TC4 TC4 800