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The working fluid state at point 8 is determined using the previously discussed energy balance on the recuperator. The enthalpy and entropy for point 8 are known and the heat transfer in the condenser is calculated as: Qcond mwf hwf,8 hwf,1 (5.19) The working fluid state at the outlet of the condenser was defined at the start of the analysis as a saturated liquid at 90°C, completing the definition of the closed thermodynamic system. For the representative point, the ethanol enthalpy at point 1 is 436 kJ kg-1, the ethanol enthalpy at point 8 is 1,349 kJ kg-1, and the ethanol mass flow rate is 5.25 g s-1, yielding a condenser heat transfer rate of 4.79 kW. The thermodynamic models for the WHR systems at elevated coolant temperatures were similar to the analysis outlined for the 90°C coolant systems, with a few important differences. Therefore, only the differences will be highlighted and covered in detail. As previously mentioned, the high-temperature WHR systems differ from the 90°C systems in that the working fluid path splits after the low-temperature side of the recuperator, with one path flowing through the engine as coolant and one path flowing through an exhaust evaporator like the one described in the 90°C case. The heat transfer to the working fluid inside the engine structure is known from the experimental data, where the heat transfer in the exhaust evaporator is found using the same method outlined for the 90°C case. The sample calculations for the high-temperature coolant models will use the representative operating point of 3100 rpm, 24 N-m, 150°C coolant temperature, and 90°C condenser temperature (Table 5-6). The mass flow rate of the ethanol through each evaporator can vary with the following constraints: mwf,tot mwf,eng mwf,evap (5.20) 82PDF Image | WASTE HEAT RECOVERY FROM A HIGH TEMPERATURE DIESEL ENGINE
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