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point 6 (Table 5-5) to arrive at a superheater heat transfer rate of 2.58 kW. Equation (5.14) is then solved for the exhaust enthalpy at point 1 using the superheater heat transfer rate of 2.58 kW, the exhaust mass flow rate of 16.3 g s-1, and the exhaust enthalpy of 361 kJ kg-1 at point 2. The result is an exhaust enthalpy of 519 kJ kg-1 at point 1 for the representative test point. The maximum heat transfer rate in the superheater is then found using equation (5.15). From Table 5-5, the minimum heat capacity rate for the superheater is 13.9 W K-1, the exhaust temperature at point 1 is 500.6°C, and the ethanol temperature at point 5 is 200°C. The result is a maximum superheater heat transfer rate of 4.18 kW, which is then used to find the heat exchanger effectiveness (equation (5.16)) of 62%. The key result of the thermodynamic models is the power output from the turbine expander. The power output is found using the isentropic efficiency of the turbine, which is defined as follows: hwf,6 hwf,7 (5.17) hwf,6 hwf,7,s Using the isentropic efficiency for the turbine of 60% (given in Table 5-2), and the theoretical isentropic enthalpy of the ethanol at point 7 of 1,548 kJ kg-1, and the ethanol enthalpy of 1,846 kJ kg-1 at point 6, the enthalpy at point 7 is found to be 1,667 kJ kg-1. The enthalpy difference across the turbine is then used to determine the power output: Wturb mwf hwf,6 hwf,7 (5.18) From the previous calculations, the ethanol enthalpy at point 6 and 7 for the representative operating condition are 1,846 kJ kg-1 and 1,667 kJ kg-1, respectively. From Table 5-5, the ethanol mass flow rate is 5.25 g s-1, yielding a turbine power output of 0.94 kW. η turb,s 81PDF Image | WASTE HEAT RECOVERY FROM A HIGH TEMPERATURE DIESEL ENGINE
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