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temperature WHR systems (Figure 5-2) build upon the state-of-the-art system by adding the engine coolant passages as a second evaporator that runs in parallel with the exhaust evaporator. The differences between the state-of-the-art and the high-temperature WHR system models will follow, including a second sample calculation for clarity. The model for the 90°C WHR system will be described first using a thermodynamic analysis for a closed system. Sample calculations will be presented using the representative point data provided in Table 5-5. At point 1 for the working fluid, the state is defined by the condenser temperature (either 60°C or 90°C) and the working fluid quality of one, since we assume that the working fluid is 100% liquid at the outlet of the condenser. Table 5-5. Thermodynamic model inputs for representative point of 3100 rpm, 24 N-m, 90°C coolant temperature, and 90°C condenser temperature with WHR from exhaust only. Parameter Value Ethanol Units g s-1 kJ kg-1 °C kJ kg-1 °C kJ kg-1 kJ kg-1 kJ kg-1 kJ kg-1 kJ kg-1 kJ kg-1 g s-1 kJ kg-1 K-1 °C kJ kg-1 W K-1 W K-1 Ethanol mass flow rate Isentropic ethanol enthalpy at point 2 Ethanol temperature at point 3 Ethanol enthalpy at point 4 Ethanol temperature at point 5 Ethanol enthalpy at point 6 Ethanol enthalpy at point 7 Isentropic ethanol enthalpy at point 7 Ethanol enthalpy at point 8 Theoretical ethanol enthalpy at T7 and P3 Theoretical ethanol enthalpy at T2 and P8 Exhaust Exhaust mass flow rate Exhaust specific heat capacity rate in single-phase evaporator Exhaust temperature at point 1 Exhaust enthalpy at point 4 Other Minimum heat capacity rate for evaporator (single-phase) Minimum heat capacity rate for superheater 5.25 440 180 850 200 1,846 1,667 1,548 1,349 1,621 1,269 16.3 1.08 500.6 170 17.6 13.9 77PDF Image | WASTE HEAT RECOVERY FROM A HIGH TEMPERATURE DIESEL ENGINE
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