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4-5 Heat Exchanger results 49 fluid and the process parameters. The only significant difference is the slightly lower power output and net efficiency. The final selection of the working fluid should be based on the optimization of the overall conversion performance, rather than solely on the optimization of the turbine efficiency. However, it should be noted that lower turbine efficiencies increases the load on the condenser [28]. The incorporation of a preliminary design model gives an idea of the dimensions of the turbine and governs the optimization and hence is recommended. 4-5 Heat Exchanger results Table 4-6: Comparative analysis of the heat exchanging equipment results Heat Transmitted [kJ/s] High terminal temperature difference[oC] Low terminal temperature difference [oC] Pinch point temperature difference [oC] UA [W/K] Heat Transmitted [kJ/s] High terminal temperature difference[oC] Low terminal temperature difference [oC] Pinch point temperature difference [oC] UA [W/K] Heat Transmitted [kJ/s] High terminal temperature difference[oC] Low terminal temperature difference [oC] Pinch point temperature difference [oC] UA [W/K] Heat Transmitted [kJ/s] High terminal temperature difference[oC] Low terminal temperature difference [oC] Pinch point temperature difference [oC] UA [W/K] Hypothetical Optimum Fluid Exhaust gas evaporator 26.31 46.18 25 21.75 0.762 EGR evaporator 32.01 168.18 25 25 0.426 47.89 5 17.00 5.00 4.88 32.33 37.87 25 25 1.043 Real Optimum Fluid D4 24.64 25.32 51.80 64.5 25 25 16.83 25 0.669 0.608 31.07 31.45 173.80 186.50 25 25 25 25 0.405 0.391 45.61 47.15 5 5 16.54 20.27 5.00 5 4.73 4.32 35.50 33.88 37.21 35.42 25 25 25 25 1.156 1.133 Condenser Regenerator Table 4-6 presents a comparison of the heat exchanging equipments for each fluid. As discussed earlier, the higher evaporator temperatures in the optimal fluids reduces the amount of heat that can be extracted from the flue gas. Hence the heat transmitted is lower in case of the optimal fluids when compared to D4. Also, the condenser has the highest UA value among all the heat exchangers which implies a larger area is required. This is mainly because of the high volumetric flow due to relatively lower density from the turbine outlet which has to be cooled. Figure 4-11 illustrates a comparison of the Q-T diagrams for the evaporators with respect to the work of Lang et. al. [21] who provide only one diagram for the evaporator and hence it is assumed to be the exhaust gas evaporator. The pinch point temperature difference is lower in this work for the exhaust gas evaporator illustrated in Figure 4-11(a) when compared to the work of Lang in Figure 4-11(c). The exhaust gas heat exchanger has a lower exergy loss than the evaporator designed in the paper. The exergy loss is considerably higher in the EGR evaporator as both the evaporators are assumed to have the same pressure and outlet temperature. This loss can be reduced by varying the pressure and temperature in the EGR evaporator but it can lead to issues in control of the system. Master of Science Thesis Akshay HattiangadiPDF Image | Working Fluid Design for Organic Rankine Cycle
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