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Condenser (b) 3% Turbine 63% Pump 2% RHE 0% Evaporator 32% (a) Turbine 64% Condenser 3% Pump 2% Evaporator 31% Open (c) Pump 1 Feedliquid Pump 2 1% 1% 8% Condenser 3% Turbine 69% Evaporator 18% (d) Closed Feedliquid Pump 1 7% 2% Condenser 3% Pump 2 0% Mixing Unit 0% Evaporator 19% Turbine 69% Figure 5.6 - Exergy loss distribution: (a) simple Rankine engine, (b) Rankine engine with regenerative heat exchanger, (c) Rankine engine with open feedliquid heater and (d) Rankine engine with closed feedliquid heater 5.4.1.2 Configuration 2 - Rankine engine with regenerative heat exchanger The role assigned to the regenerator is to increase the average evaporator temperature. From Table 5.2b it can be seen that the temperature at the evaporator inlet (point 6, 31.04 oC) is lower than temperature at the pump outlet (point 5, 31.98 oC) which means that the heat exchanger cools instead of heats. From the results displayed in Table 5.3, it can be seen that the regenerator has a very small coefficient of influence (0.05%) which means very little effect on the system. And of course, the exergy efficiency of the system in comparison with the simple Rankine engine is unchanged and the degree of thermodynamic perfection is slightly decreased, by 8%. Unnecessary use of regenerator can be drawn as conclusion confirming the uselessness of this device when the working fluid is an isentropic one such as R134a. No exergy is destroyed in the regenerator and the exergy loss distribution is similar to that of the basic engine (Figure 5.6b). The evaporator is still the most important component with a coefficient of influence of 32.53% followed by the turbine. Page | 124PDF Image | Low-Grade Heat Conversion into Power Using Small Scale Organic Rankine Cycles
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