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106 7 Waste heat recovery of large scale reciprocating engine Table 7.2: Case study results. EG heat recovery 395 ◦C-130 ◦C heat rate to evaporator ORC power output ORC electric efficiency increase in power plant electric power output CA heat recovery 210 ◦C-85 ◦C heat rate to evaporator ORC power output ORC electric efficiency increase in power plant electric power output 7921 kW 1895 kW 23.9 % 11.4 % 3333 kW 394 kW 11.8 % 2.4 % the turbine replaced with a pressure reduction system, and thus, no power was extracted from the system. The main technical data of the test engine is presented in Table 7.3. Table 7.3: Technical data of the test engine. Electric power output Rotational speed Number of cylinders Cylinder inner diameter Power/cylinder Mean effective pressure Charge air mass flow rate Compressor pressure ratio Compressor efficiency Charge air temperature at compressor outlet 1640 kW 750 rpm 4 320 mm 410 kW 22.97 bar 3.14 kg/s 3.43 c. 80 % 185 ◦C The aim of the tests was to study especially the performance of the evaporator acting as a charge air cooler, and thus, to validate the simulated potential on producing additional power from the charge air heat. A layout of the experimental setup is presented in Figure 7.10 and a schematic process diagram in Figure 7.11, presenting the main components of the system as well as the locations of pressure, temperature, and mass flow measurements. The evaporator was located inside the engine hall near the engine turbocharger, and the intercooler of the en- gine was installed after the evaporator to further cool down the charge air before it enters the engine. The rest of the experimental setup; namely the expansion valve, recuperator, condenser, condensate tank, and the feed pumps; were located outside the engine hall. Commercial heat exchangers of plate and shell type were used in the experimental setup.PDF Image | WORKING FLUID SELECTION AND DESIGN OF SMALL-SCALE WASTE HEAT RECOVERY SYSTEMS BASED ON ORGANIC RANKINE CYCLES
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