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Energies 2020, 13, 4014 5 of 18 correspond to the maximum value of η. In any case, the considerations of this case are also extended to cycles with different compression ratios. Figure 3. Thermodynamic cycle efficiency ηth and total efficiency η = ηthφ as a function of the maximum cycle pressure for different maximum cycle temperatures T4. The results are for simple recuperative supercritical carbon dioxide cycles. The heat source is cooled from TH1 = 350 ◦C to TH2 = 217 ◦C (φ ≈ 0.6) and the remaining potentially available thermal energy (from TH2 to TH0 ≈ 51 ◦C) is lost. The transferred heat in the recuperator is about 2.5 times greater than the net power, and the air mass flow required at the radiator is almost 10 times that of the carbon dioxide circulating in the engine. The high power required by the ventilators could affect the system efficiency and the radiator—i.e., one of the major cycle components. The assumed constraint of an MITAC equal to 20 ◦C results in a temperature T1 of 35 ◦C (corresponding to a reduced temperature Tr of 1.01). These results seem consistent with those obtained in [15], considering that the authors assumed a maximum cycle pressure of 200 bar and a relatively high recuperator efficiency of 95% (five points higher than the efficiency resulting from the present analysis). Figure 4. The simple carbon dioxide thermodynamic cycle shown in Figure 2 and the heat sources in a plane of temperature–dimensionless transferred power. More advanced plant configurations (with a single split, a dual split and possibly with an intercooler) were not considered here. They performances and a detailed description of the plantPDF Image | CO2 Mixtures as Working Fluid for High-Temperature Heat Recovery
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