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International Journal of Materials, Mechanics and Manufacturing, Vol. 1, No. 1, February 2013 anergy ratio due to exhaust of source fluid for the working fluids. As turbine inlet pressure increases, the anergy ratio increases at a certain rate, and after a certain point its increasing rate becomes lower. This can be explained as follows. As the turbine inlet pressure increases, the corresponding saturated temperature also increases, which causes the exit temperature of source fluid higher. Then, the temperature difference between fluid streams increases in the heat exchanger, so exergy destruction does. However, when the turbine inlet pressure increases to a certain value at which the working fluid entering the heat exchanger as saturated liquid, the increasing rate of exit temperature of source fluid becomes smaller or even minus. For a specified value of the turbine inlet pressure, the anergy ratio for iso-pentane or normal pentane is high, but that of R143a or ammonia is relatively low. The anergy ratio due to exhaust of source fluid is the greatest among the components of the system. 15 10 5 0 10 20 30 40 50 Turbine inlet pressure [bar] Fig. 6. Anergy ratio of turbine and pump 60 50 40 30 20 10 0 10 20 30 40 50 Turbine inlet pressure [bar] Fig. 7. Exergy efficiency For various working fluids, Fig. 6 and Fig. 7 show the effect of turbine inlet pressure on the anergy ratio of turbine/pump and exergy efficiency, respectively. As it is seen in the figures, the anergy ratio of mechanical work of turbine and pump is approximately proportional to the exergy efficiency, since in this work isentropic efficiencies of turbine and pump are assumed to be constant for various values of system parameters. The increase in the turbine inlet pressure has positive or negative effect on the exergy efficiency, which is dependent on the working fluid. As turbine inlet pressure increases, the exergy efficiency increases for ammonia, R134a, R22, iso-butane, R152a, R143a, and butane. But it decreases for iso-pentane and normal pentane. Fig. 7 also shows that the working fluid which has the maximum exergy efficiency varies with turbine inlet pressure. IV. CONCLUSIONS In this paper, the exergetical performance of organic Rankine cycle with internal heat exchanger has been analyzed based on the second law of thermodynamics. The anergy ratio at source heat exchanger or regenerator decreases monotonically with increasing turbine inlet pressure for all fluids. For ammonia, the anergy ratio at heat exchanger is the greatest among the components of the system. However, the anergy ratio at regenerator is the greatest for R143a, while the anergy ratio of exhaust is the greatest for iso-pentane or normal pentane. Exergy efficiency generally increases with turbine inlet pressure for such as ammonia or R134a, but decreases for iso-pentane and normal pentane. For a given source temperature, working fluid which has the maximum exergy efficiency varies with turbine inlet pressure. ACKNOWLEDGMENT This paper was supported by Research Fund, Kumoh National Institute of Technology. REFERENCES [1] N. A. Lai, M. Wendland, and J. Fisher, “Working fluids for high temperature organic Rankine cycle,” Energy, vol. 36, pp. 199-211, 2011. [2] K. H. Kim, C. H. Han, and K. Kim, “Effects of ammonia concentration on the thermodynamic performances of ammonia-water based power cycles,” Thermochimica Acta, vol. 530, pp. 7-16, 2012. [3] T. C. Hung, T. Y. Shai, and S. K. Wang, “A review of organic Rankine cycles (ORCs) for the recovery of low-grade waste heat,” Energy, vol. 22, pp. 661-667, 1997. [4] U. Drescher and D. Brueggemann, “Fluid selection for the organic Rankine cycle (ORC) in biomass power and heat plants,” Applied Thermal Eng., vol. 27, pp. 223-228, 2007. [5] Y. Dai, J. Wang, and L. Gao, “Parametric optimization and comparative study of organic Rankine cycle (ORC) for low grade waste heat recovery,” Energy Convs. Mgmt., vol. 50, pp. 576-582, 2009. [6] F. Heberle and D. Brueggemann, “Exergy based fluid selection for a geothermal organic Rankine cycle for combined heat and power generation,” Applied Thermal Eng., vol. 30, pp. 1326-1332, 2010. [7] B. F. Tchanche, G. Papadakis, and A. Frangoudakis, “Fluid selection for a low- temperature solar organic Rankine cycle,” Applied Thermal Eng., vol. 29, pp. 2468-2476, 2009. [8] T. C. Hung, S. K. Wang, C. H. Kuo, B. S. Pei, and K. F. Tsai, “A study of organic working fluids on system efficiency of an ORC using low-grade energy sources,” Energy, vol. 35, pp. 1403-1411, 2010. [9] K. H. Kim, “Effects of superheating on thermodynamic performance of organic Rankine cycles,” WASET, vol. 78, pp. 608-612, 2011. [10] K. H. Kim, “Thermodynamic performance of regenerative organic Rankine cycles,” WASET, vol. 59, pp. 1515-1519, 2011. [11] K. H. Kim and C. H. Han, “Analysis of transcritical organic Rankine cycles for low-grade heat conversion,” Adv. Sci. Lett., vol. 8, pp. 216-221, 2012. [12] K. H. Kim and H. J. Ko, “Exergetical performance assessment of organic Rankine cycle with superheating,” App. Mech. Materials, vol. 234, pp. 69-73, 2012. NH3 R134a R22 iso-C4H10 R152a R143a C4H10 iso-C5H12 n-C5H12 NH3 R134a R22 iso-C4H10 R152a R143a C4H10 iso-C5H12 n-C5H12 44 Exergy efficiency [%] Anergy ratio of turbine and pump [%]PDF Image | Exergy Analysis of Organic Rankine Cycle with Internal
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