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Vélez et al / DYNA 81 (185), pp. 153-159. June, 2014. isentropic efficiencies of 75% are assumed for the pump as well as for the turbine. The cycle’s total energy efficiency is: (1) is the ( 2 ) ( 3 ) (4) t power input in the pump defined as: W m h h t 12 Q m h h e 14or Qmhh e 1 4IHX W W p Where Wt is the power out from the turbine; Wp Figure 2. Typical T-s diagram for a Rankine power cycle. According to the state points displayed in Fig. 1, Fig. 2 shows the power cycle in a T-s-diagram plotted with [32] data. As an example, an ideal cycle process is shown by segments, which are built from the state points 1, 2is, 3 and 4is marked with (○). The line segment 1-2is represents an isentropic expansion with a production of output work. Heat is extracted from 2is to 3 along a constant subcritical pressure line. Then, an ideal compression of the saturated liquid from pressure at state point 3 to state point 4is. Finally, the segment 4is-1 represents the heat addition at constant subcritical pressure to the highest temperature of the cycle at state point 1. The previous case, but operating under conditions in which the expansion process as well as compression process have a certain efficiency, is represented by the segments built from the state points 1, 2, 3 and 4 marked with (○) in the same Fig. 2, which are also related to Fig. 1. In order to increase the process efficiency, an IHX is introduced (as it can be seen in Fig. 1), in which a portion of the rejected heat, represented by an enthalpy drop from 2 to 2IHX at constant subcritical pressure, is transferred back to the fluid, raising its enthalpy from 4 to 4IHX at constant subcritical pressure. Net heat rejection is indicated by the enthalpy drop from 2IHX to 3 at constant subcritical pressure. State point 3 is at the lowest temperature of the cycle and above the temperature of the heat sink. Net input heat to the cycle occurs from 4 (or 4IHX) to 1 at constant pressure. Net output work is the difference between the output work from state points 1 to 2 and the input work pump from state points 3 to 4. 3. Modelling of the process The equations used to determine the performance of the different configurations are presented in this section. Using the first law of thermodynamic, the performance of a Rankine cycle can be evaluated under diverse working conditions. For both configurations, the analysis assumes steady state conditions, no pressure drop or heat loss in the evaporator, IHX, condenser or pipes, and the constant An input temperature of the condensation water T7=15oC and a minimum working fluid condensation temperature of T3=25oC have been considered. Otherwise, a pinch point of 10oC is maintained between T3 and the output temperature of the condensation water (T8) for both configurations. 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. The minimum discharge pressure of the turbine (P2) is equal to the saturation pressure of the fluid in liquid state (P3) to the temperature T3=25oC. The thermodynamic analysis of the cycle was performed using a process simulator HYSYS® (Hyprotech Co., Canada). This simulator is useful for thermodynamic analysis, especially at steady state condition, and it has the advantage of including fluid properties and ready to use optimization tools. Its predictions have been compared with the ones from [32] and the results are very similar. The simulation flow diagram is the same as the one presented in Fig. 1, and the method for resolving all the components is widely described in [3,10]. 4. Results and discussion This section presents the results obtained in the simulations done with R134a fluid using the method described in section 3. As it was commented in the introduction, this fluid is of interest for the temperature range under study because of its good environmental characteristics, safety and thermophysical properties (temperature and critical pressure, boiling point, etc.). Furthermore, it must be taken into account that the ideal working fluid for a Rankine cycle is that whose saturated vapor line is parallel to the line of expansion of the turbine. As a consequence, a maximum efficiency is ensured in the 155 W m h h Qe p34 and the Qe is the heat input in the evaporator defined as:PDF 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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