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Table 5-3. Matrix of WHR operating points modeled. Engine Speed [rpm] Torque [N-m] % of Max Load Coolant Temp [°C] Condenser Temp [°C] 60 90 3100 24 74% 90 X X 150 X X 175 X X 200 X X efficiency is then compared to the baseline efficiency of the 90°C coolant temperature for consistency. The inputs for the thermodynamic analysis are shown in detail in Table 5-2 for each coolant temperature modeled. The first section of the table lists the inputs pulled directly from the experiment data for the temperatures, flow rates, and measured heat transfer rates to the exhaust and coolant. The second section of the table shows the values that were inputs for the model, such as the evaporator saturation temperature and the maximum superheat temperature. Note that the values may differ between the two condenser temperatures that were modeled. Each model was optimized to produce the maximum output and still maintain a minimum CAT of approximately 5°C for each heat exchanger. The CAT was allowed to occur at any location, including the inlet of the heat exchanger. Optimization was accomplished by adjusting the maximum superheat temperature (see Figure 5-4). The superheat temperatures were kept under a maximum of 375°C for all configurations. The thermodynamic models were created using several assumptions and simplifications. Table 5-1 summarizes the assumptions for values such as the heat exchanger effectiveness and isentropic efficiency of the pump and turbine. In addition to these assumptions, it was also assumed that no exhaust aftertreatment would be used since the test engine is a Tier 0 diesel engine with minimal emission standards. Therefore, no effort was made to ensure that exhaust temperatures would be sufficiently high after the exhaust evaporator for adequate operation of an aftertreatment 74PDF Image | WASTE HEAT RECOVERY FROM A HIGH TEMPERATURE DIESEL ENGINE
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