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72 Integrated system design 10 0 −10 −20 −30 −40 −50 −60 6.96 6.965 6.97 s [kJ/kgK] 6.975 6.98 Pressure Density Enthalpy Cycle 00=02 0 013 19 =019 Cycle points Environm. cond. (0) Fan inlet (02) Fan outlet (013) Nozzle outlet (19) Shaft power [kW] Isent. efficiency Pressure ratio PTh [bar] [◦ C] 0.24 -54.50 0.38 -22.80 0.46 -6.72 0.24 -53.00 16063.54 0.89 1.21 [kJ/kg] 218.79 250.56 266.69 220.29 Figure 4-4: Fan T-s diagram of the Turbofan Trent 1000 engine. The energy entering the cycle is taken from the fuel energy input reported in Table 4-2. Consequently, the enthalpy at the inlet of the turbine, h04, can be obtained from the energy balance on the combustion chamber, h04 = h03 + fFLLHVFLηCC . (4-31) fCR The enthalpy of the air leaving the turbine can be calculated from the internal energy balance in the system. Both the fan and the compressor are driven by the high and low pressure turbines, W ̇ 2−13 + W ̇ 2−3 = W ̇ 4−5, (4-32) where W ̇ 2−13 corresponds to the shaft power of the fan, calculated in the fan analysis and shown in Figure 4-4. Likewise, W ̇ 2−3 stands for the power of the compression process from the inlet of the fan to the outlet of the compressor, while W ̇ 4−5 is the power of the high pressure Figure 4-5: Schematic T-s diagram of the core side of a turbofan engine. J.S. Bahamonde Noriega Master of Science Thesis T [◦C]PDF Image | Design method for s-CO2 gas turbine power plants
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