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Z. Shengjun et al. / Applied Energy 88 (2011) 2740–2754 2741 Nomenclature A ALT AE CC COM cp cp dM di do dry f G Gr h hLG I_ k LEC m_ r m_ w ; h m_ w ; c M Nu P Pr Q_ Re s T t tc,wi tc,wo th,wi th,wo tmax tpinch v V VER W_ W_ max wet x area of the heat exchangers (m2) atmosphere life time annual energy production of the plant (kW) capital cost of the plant ($) O&M cost of the plant ($) specific heat at constant pressure (J/(kg K)) Averaged over cross-section specific heat at constant pressure mean inner diameter (m) tube inner diameter (m) Tube outer diameter (m) dry fluid fraction factor mass flux (kg/(m2s)) Grashof number specific enthalpy (kJ/kg) isobaric latent heat of condensation (J/kg) irreversibility (kW) thermal conductivity (W/(m K)) levelized energy cost ($/(kW h)) the mass flow rate of working fluid (kg/s) the mass flow rate of geothermal water (kg/s) the mass flow rate of cooling water (kg/s) molecular weight (g/mol) Nusselt number pressure (MPa) Prandtl number heat rate injected or rejected (kW) Reynolds number specific entropy (kJ/(kg K)) temperature (K) temperature (°C) inlet temperature of heat sink (°C) outlet temperature of heat sink (°C) inlet temperature of heat source (°C) outlet temperature of heat source (°C) turbine inlet temperature (°C) the temperature difference in the pinch point of heat ex- changer (°C) specific volumes of working fluid (m3/kg) volume flow rates of working fluid (m3/h) vapor expansion ratio the power produced or consumed (kW) maximum theoretical power (kW) wet fluid vapor mass quality Xtt Lockhart-Martinelli number Greek Symbols a heat exchange coefficient (W/(m2 K)) e void fraction gI thermal efficiency gII exergy efficiency ggt generator efficiency grp working fluid pump efficiency gr recovery efficiency gst isentropic efficiency of the turbine gwp heat transfer fluid pump efficiency l dynamic viscosity (m2/s) q density (kg/m3) /v two-phase friction loss n Darcy friction coefficient D difference Subscripts b bulk B free convection bp normal boiling point c condenser cri critical F forced convection h evaporator/vapor generator H heat source in inlet of the turbine Isen isentropic fluid out outlet of the turbine l liquid L heat sink p pump pl plant r refrigerant fluid Sub subcritical t turbine tot total Tran transcritical v vapor w heat transfer fluid wl wall ww wet wall region 0 ambient 1,2,4,5 inlet of turbine, condenser, pump, vapor generator, respectively fluid. Dai [5] compared the performance of 10 pure working fluids and R236ea offered the highest exergy efficiency. Aleksandra [6] investigated the use of the 80–120 °C geothermal water in an ORC power plant and R236fa was recommended as the excellent fluids. Gu [7] conducted the experiment with the inlet temperature of hot water 75–100 °C and R600a was proved as a favorable work- ing fluid. Mago [8] performed first- and second-low analysis on R134a, R113, R245ca, R245fa, R123, R600a and R290. Hung [9] studied the ORC systems using refrigerant- and benzene-series flu- ids as working fluids. Chen [10] presented a review of the organic Rankine cycle and tanscritical power cycle and 35 working fluids were screened for the two cycles. Rayegan [11] investigated 115 fluids in the Refprop 8.0 database to screen suitable working fluid for solar ORC system. Li [12] used R123 in a novel solar ORC sys- tem. Moreover, a series of mixtures [13–18], which could be used to reduce the system irreversibilities, were also proposed in sub- critical ORC system. Due to the variable temperature of the transformation from li- quid to vapor in the vapor generator, transcritical power cycle provided a high potential in utilizing the geothermal and reducing the irreversibility. So it is theoretically the ideal cycle for the heat sources when a variable temperature is obtained during the heat exchanging process [19]. Zhang [20–23] conducted thermody- namic analysis and experiment investigation of CO2-based Ran- kine cycle powered by solar energy. It was found that CO2 could efficiently convert the low-temperature solar energy into electric- ity and hot water. Cayer [24] conducted a detailed analysis of a carbon dioxide transcritical power cycle using an industrial low- grade stream of process gases as its heat source. Schuster et al. [25] conducted energy and exergy analysis for various fluids inPDF Image | Performance comparison and parametric optimization of subcritical Organic Rankine Cycle (ORC) and transcritical power cycle system for low-temperature geothermal power generation
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