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law efficiency is shown on the right vertical axis. The graphs show the 2nd law efficiencies in the cooling cycle are much lower than those in the power cycle. This can be attributed to the relatively larger temperature differences designed into the cooling cycle heat exchangers, i.e. the evaporator and condenser, in order to minimize component size and weight. In the computational runs, the fluid exiting the boiler was maintained at saturated vapor conditions as the pump outlet pressure was varied. For investigating the superheat effects, the pump outlet pressure was set at 2,750 kPa. According to Fig. 5, pump outlet pressure has little effects on the 2nd law cycle efficiencies, while the 2nd law efficiencies decrease slightly with the fluid temperature (superheat) coming out of the boiler. This is because a fixed 20 °C of difference between the average heating source temperature and fluid temperature coming out of the boiler was given as an input. If the average temperature of the heating source is a fixed value instead, an increasing trend of the 2nd law efficiency for the power cycle would be expected as the boiler outlet pressure/temperature increased. This is because entropy generation decreases as the temperature difference in the boiler decreases. To minimize the size and weight increase of the boiler as a result of a smaller driving temperature difference, a boiler based on microchannels with an enhanced heat transfer coefficient was designed. The effects of expander isentropic efficiency and recuperator effectiveness are shown in Fig. 6. There is practically no change of 2nd law efficiency in the cooling cycle. Apparently, expander isentropic efficiency has the most impact on the 2nd law efficiency of the power cycle (as already described in a previous section), while increasing effectiveness of the recuperator also steadily increases the 2nd law efficiency. This indicates that internal recuperation is beneficial when there is sensible heat available after expansion. With a drying fluid running at superheat, there is always a significant amount of sensible heat left after the expander. The recuperator essentially delivers a higher temperature liquid to the boiler, thus reducing entropic generation during the heat input process. The effects of condensing temperature and subcooling on 2nd law efficiencies are plotted in Fig. 7. Both the power and cooling cycle 2nd law efficiencies decreased as the condensing temperature is increased (maintaining the surroundings temperature constant). This again results from the larger temperature difference between the condensing fluid and the atmosphere thus causing an increase in entropy generation. As more subcooling (lower Tsub) is incorporated into the vapor compression cycle condenser, higher 2nd law efficiency is obtained as a result of less entropy generated through the thermostatic expansion valve. 12PDF Image | Performance of a Combined Organic Rankine Cycle
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