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110 7 Waste heat recovery of large scale reciprocating engine 300 250 200 150 100 10 15 20 25 30 Evaporator outlet pressure, [bar] R245fa isopentane 150 100 50 0 10 15 20 25 30 (a) Evaporator outlet pressure, [bar] (b) 1.2 1 0.8 0.6 0.4 0.2 0 10 15 20 25 30 Evaporator outlet pressure, [bar] R245fa isopentane (c) Figure 7.14: Measured heat rate to the evaporator (a), charge air temperature at the evaporator outlet (b), and working fluid mass flow rate (c) with different evaporator outlet pressures at full engine load. loads, when compared to engine full load conditions. The pinch point temperature differ- ence in the evaporator increases as the evaporation pressure and the engine load increases, mainly due to the higher flow rates at the charge air and working fluid side at higher en- gine loads. The measured working fluid mass flow rate and the evaporator outlet pressure are presented in Figure 7.16a and Figure 7.16b. The results indicate that significantly lower working fluid mass flow rate and low evap- orator outlet pressure are obtained at engine part loads, showing almost linear behaviour as a function of engine power. As a conclusion the results indicate that the availability to produce additional power from charge air at engine part loads is significantly lower when compared to full engine loads caused by the lower amount of heat introduced to the evaporator resulting to low working fluid mass flow rate and lower temperature level R245fa isopentane Working fluid mass flow rate, [kg/s] Heat rate to evaporator, [kW] o Charge air outlet temperature, [ C]PDF Image | WORKING FLUID SELECTION AND DESIGN OF SMALL-SCALE WASTE HEAT RECOVERY SYSTEMS BASED ON ORGANIC RANKINE CYCLES
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