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7.2 Experimental results for charge air utilization 111 200 150 100 50 0 50 60 70 80 90 100 Engine load, [%] CA outlet T CA inlet T 300 250 200 150 100 50 0 50 60 70 80 90 100 (a) Engine load, [%] (b) 20 15 10 5 0 50 60 70 80 90 100 Engine load, [%] R245fa (c) Figure 7.15: Measured charge air temperature at the evaporator inlet and outlet (a), heat rate to the evaporator (b), and pinch-point temperature difference in the evaporator (c) at engine part loads and at full engine load. of the charge air leading to lower cycle efficiency. This is important to take into account especially when considering the use of charge air heat utilization in engines operating frequently at part load conditions. 7.2.5 Process with pressure reduction system replaced with a turbine Based on the measured results, the power output of the system was estimated in a case when the pressure reduction system is replaced with a turbine-generator having the tur- bine with an isentropic efficiency of 80 % and other process values were evaluated based on the measurement results. If the process would be equipped with a turbine-generator, power would be extracted from the expansion leading to lower vapour temperature at the recuperator inlet as well as to lower liquid temperature at the evaporator inlet, when compared to the measured values with process with the pressure reduction system. If a R245fa ∆T in the evaporator, [oC] pp o Charge air temperature, [ C] Heat rate to evaporator, [kW]PDF Image | WORKING FLUID SELECTION AND DESIGN OF SMALL-SCALE WASTE HEAT RECOVERY SYSTEMS BASED ON ORGANIC RANKINE CYCLES
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