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ORC increases with TIP but the maximum mechanical work output is achieved at P3 1⁄4 25:59 bar for R134a and at 6.19 bar with R245fa as the working fluid. The range of TIP for which the calculations were performed is limited by the physical limits of the working fluids imposed by REFPROP and boundaries imposed in the model as described in Section 3. In the case of the hot brines, only results calculated for R134a, R245fa and n-pentane fall within these limits, and are presented in Figure 5. The existence of a maximum work output relates to the amount of heat that can be input into the cycle as the operating conditions vary. The Aneke et al.’s study also shows similar trends [3]. Figure 6 shows plots of the temperature of the two fluid streams as they flow along the heat exchanger (this distance is expressed in terms of the enthalpy exchange between the fluid streams in the figure), for the Ninian oil field hot brine case with R245fa. The three plots are at the different locations labelled in Figure 5. These are below the maximum work output (Cycle A, Figure 6a), at the maximum (Cycle B, Figure 6b) and above the maximum (Cycle C, Figure 6c). The plots show how heat input decreases as TIP increases, as seen in Figure 5b. As TIP increases, from Cycles A–C, a smaller temperature drop occurs across the heat source stream in Figure 6, so less heat energy is transferred into the ORC working fluid. Figure 7 shows the temperature entropy plots for Cycles A, B and C. Cycle C is the most thermally efficient, and Cycle A is the least thermally efficient. A larger amount of work is produced by Cycle B than by Cycle A, because the increase in efficiency out- weighs the decrease in heat energy into the cycle. After Point B heat input to the cycle decreases more rapidly as TIP increases, due to the change in pinch point location. So for Cycle C, the gain in efficiency of the cycle is outweighed by the reduction in heat into the cycle and less work output is produced. These figures demonstrate that an optimum balance between heat Figure 7. Temperature entropy diagrams for cycles A, B and C labelled in Figure 5. input into the cycle and thermal efficiency, of the cycle must be reached in order to maximize the work output. Work output for each waste heat source can be compared by considering Figures 5c, 8b and 10b. Some working fluids mod- elled in the hot brine and industrial waste steam cases show a curve that has an optimum TIP, where work output is maximum. But others, for example the diesel engine results (Figure 10b), show an increase in work output with TIP for all working fluids simulated, in the case of the fully loaded engine. In all cases, the ORC configuration varies from subcritical or tri- lateral to superheated, but the optimum cycle configuration, with respect to work output, is not common in all cases. The trend of these plots can be explained by examining the location of the pinch point and the effect this has on the heat input to the cycle, in each case. Figure 8. Plots of heat input (a) and mechanical work output (b) against TIP for the industrial steam case (Table 1). Organic Rankine cycles in waste heat recovery International Journal of Low-Carbon Technologies 2013, 8, i9–i18 i15 Downloaded from https://academic.oup.com/ijlct/article/8/suppl_1/i9/771990 by guest on 13 January 2021PDF Image | Organic Rankine cycles in waste heat recovery
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