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Figure 7. Influence of the P1/P2 ratio on the overall efficiency of the cycle for the overheated fluid at T1=70oC. Figure 8. Influence of the P1/P2 ratio on the overall efficiency of the cycle for the overheated fluid at T1=60oC. T1 of 101oC. For pressures less than 25 bar such influence was not very significant. Also Figs. 4 to 8 show the condition of overheating causes a slight increase in efficiency compared to that achieved at saturation conditions. This occurs because the inlet temperature to the turbine has a wide range of effects on the efficiency of the system depending on the slope of the isobaric curve in the region of overheated steam on the T-s diagram. If a fluid has a significantly steeper slope in the region of high pressure isobaric curve than in the region of low pressure, the system's efficiency increases as the inlet temperature to the turbine increases, otherwise it decreases. In our case, given that the R134a fluid analysis shows a slight negative slope in the saturation curve (Fig. 2), a slight overheating causes a slight increase in η, whereas, when the ratio P1/P2 increases, much higher values of this efficiency are obtained and in addition as T1 rises, such η increases more sharply. Thus, the following section 4.3 discusses how the inlet temperature to the turbine T1 influences the efficiency of the cycle, at various constant P1/P2 ratios. 4.3. Influence of the input temperature to the turbine T1 on the efficiency of the cycle. In Fig. 9 the results on the η of the cycle by increasing the T1 at a constant P1/P2 ratio are presented. It is obvious that when the P1/P2 = 1.5 (which is the lowest of those studied, see Fig. 9) the efficiency, η, increases with T1. However, it should be noted that η is a weak function of temperature for the case of the fluid studied (as it was Figure 9. Influence of the input temperature to the turbine T1 on the efficiency of the cycle with constant P1/P2 ratio. reported in the section 4.2), i.e. overheating the inlet fluid to the turbine does not cause a significant change in η. However, much higher values of η are obtained when the P1/P2 ratio increases and also as T1 rises, η increases more sharply as it is shown in Fig. 9. 4.4. Comparation of basic ORC vs. other with IHX Finally, Fig. 10 presents the results of simulations realized with a basic and with an IHX ORC (Fig. 1). The inlet pressure varies from 7 bar up to its critical pressure at four constant inlet turbine temperatures: 150°C, 120°C, 90°C and 60oC. Also, a pinch point of 5oC is maintained between T3 and the output temperature of the condensation water (T8) and a temperature difference (∆T) between T2 and T4 of at least 5oC for the cycle with IHX. In the heating process, the overheating of the inlet fluid to the turbine (T1) is considered from the condition of saturated steam up to its critical temperature. In Fig. 10, the blue tendency lines and the open blue symbols indicate the energy efficiencies of the simple cycle, the green tendency lines and the green bold symbols point to the energy efficiencies of the cycle with IHX and the discontinuous red lines represent the net specific work (wne). On the other hand, symbols represented with a triangle (▲), square (■), circle (●) and rhombus (♦) are linked with the analyzed temperatures of 150oC, 120oC, 90oC and 60oC, respectively. Figure 10. Energy efficiency (η) with IHX (bold symbols) and without IHX (open symbols), and net specific work (wne) produced (discontinuos lines) vs. Pressure P1 for T1=150oC (▲), T1=120oC (■), 90oC (●), and 60oC (♦). Vélez et al / DYNA 81 (185), pp. 153-159. June, 2014. 157PDF Image | Thermodynamic analysis of R134a in an Organic Rankine Cycle for power generation from low temperature sources Analisis termodinamico del R134a en un Ciclo Rankine Organico para la generacionde energía a partir de fuentes de baja temperatura
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