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Chena Geothermal Power Plant Project Prepared for the Alaska Energy Authority 4.2 Refrigerant Design Points Mass flow rate: Evaporator/turbine inlet pressure: Condenser/turbine exit pressure: Turbine gross power: Pump power: System output power (net): Thermal efficiency: Final Report January, 2007 This efficiency is quite a challenge given the limited thermodynamic availability of the low temperature geothermal heat source. A completely reversible thermodynamic cycle working with the same heat source and heat sink temperature glides would have a thermal efficiency just under 18%. Fortunately, efficiency improvements are far less critical in power generation when the fuel is essentially free. 26.8 lbm/s 232 psia 63.6 psia 250 kW 40 kW 210 kW 8.2 % 1 TS Cycle Diagram of an Unrecuperated ORC System for Chena Hot Springs Application 0.165 0.185 250.0 200.0 150.0 100.0 50.0 0.0 0.2000 0.2500 0.205 0.225 0.245 Entropy (water side) (Btu/(lbm R) 250 200 150 100 50 0 Geothermal Resource A B R134a 1 4 2 3 C Cooling Water D 0.3000 0.3500 0.4000 0.4500 Entropy (R134a side) (Btu/(lbm-R)) Figure 5: TS Cycle Diagram for the Chena Hot Springs Power Plant A TS Cycle Diagram for the power plant is included in Figure 5. On the preheater/evaporator side of the ORC system, 530 gpm of 164 °F hot water (point A in Figure 5) enters the unit and is cooled to 130 °F (point B) transferring 2.58 MW of thermal energy to the refrigerant. This energy preheats the 26.8 lbm/s refrigerant mass flow rate from 54 °F (state point 4) to 136 °F and subsequently boils the working fluid at this temperature before slightly superheating it (state point 1). The high-pressure refrigerant vapor is expanded in the turbine that extracts 270 kW of mechanical power 13 Temperature (F) Temperature (F)PDF Image | 400kW Geothermal Power Plant at Chena Hot Springs
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