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concentration in the exhaust,CCO2 is the CO2 concentration in the exhaust, and CTHC is the concentration of THC in the exhaust (assuming methane). For the representative point, the fuel mass flow rate is 0.507 g s-1 and the LHV of diesel fuel is 43.2 MJ kg-1. The emissions concentrations are: 73.17 ppm for CTHC, 385.2 ppm for CCO, and 68,700 ppm for CCO2. From these values, equation (4.14) yields a loss of 0.28 kW from the unburned hydrocarbons measured in the exhaust. The energy balance results for the representative point are summarized in Table 4-3. The fuel input of 21.89 kW and the total measured output of 19.43 kW leaves 2.46 kW of additional fuel energy. As mentioned earlier, this energy is lost to the environment, soot in the exhaust, and pumping losses. Table 4-3. Energy balance results for representative point 3100 rpm, 18 N-m torque and 150°C coolant temperature. Input Value Units Fuel Energy Outputs 21.89 kW 5.78 kW 4.22 kW 2.42 kW 6.73 kW 0.28 kW 19.43 kW 2.46 kW Engine Power Output Coolant Waste Heat Oil Waste Heat Exhaust Waste Heat Unburned Hydrocarbons Total Other Losses 4.2 Waste Heat Availability Prior work shows that the quality of waste heat is as important as the quantity of that waste heat. The First Law of Thermodynamics is useful for evaluating energy balances, but is not sufficient to analyze a Rankine cycle and determine the possible efficiency gain for a given heat source. Here, the Second Law of Thermodynamics can be used to analyze a cycle and shed light 64PDF Image | WASTE HEAT RECOVERY FROM A HIGH TEMPERATURE DIESEL ENGINE
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