Modular Trough Power Plant Cycle and Systems Analysis

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Modular Trough Power Plant Cycle and Systems Analysis ( modular-trough-power-plant-cycle-and-systems-analysis )

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A brief review of the results of the cycles analyzed above indicates that neither the use of reheat nor the utilization of the mixed working fluids have significant impact on the performance of the cycle. Therefore, for the sake of achieving lower electricity cost and ease of operation, we will use the cycle with recuperation and pure working fluid (shown in Figure 5) for the optimization and off-design analysis. It should be pointed out that we anticipate a reasonably superior performance for the cycle with mixed working fluid when off-design (partial solar load) conditions are considered. However, in this study, because of limited resources, we did not pursue optimization of any cycle that uses mixed working fluids. Future work will address that interesting topic. The following sections discuss potential options for improving the cycle efficiency and provide a detailed off-design analysis of the cycle. 3.3 Options for Improving Cycle Efficiency The cycle shown in Figure 5 was analyzed for a condensing pressure of 20 psia (0.138 MPa) with a pinch point of 17°F (9.4°C) for the boiler and 13°F (7.2°C) for the condenser. To identify the highest efficiency that one could get for the cycle with recuperator, we decided to lower the condensing pressure to 17.5 psia (0.121 MPa), reduce the pinch point in all the heat exchangers to 5°F (2.8°C), while maintaining the turbine efficiency at 0.75. In doing so, we obtained a net cycle efficiency of 23.0%. This is a considerable improvement over the 20.1% efficiency that we were getting earlier. However, the field achievability of the specifications for this cycle need to be further verified and validated. This optimized cycle was then used as base case for our off- design studies presented in Section 3.4. 3.4 Off-Design (Partial Load) Operation and Its Impact on Performance The cycle shown in Figure 5, ORC with recuperation, was analyzed for off-design conditions. The cycle was first designed and optimized for the following base condition: air-cooled condensing with ambient temperature of 80°F (26.7°C), a solar resource that entered the heat exchanger at 580°F (304°C) and exited at 344°F (173.3°C). The working fluid was Pentane, and it was condensed at a condensing pressure of 17.5 psia (0.121 MPa). The maximum operating pressure in the heater/boiler was set at 610 psia (4.2 MPa), and the pinch point in all the heat exchangers was set to 5°F (2.8°C). The pressure drop on the cold side of the recuperator was assumed to be 10 psia (69 kPa), while it was assumed to be 2 psia (13.4 kPa) on the hot-side. The pressure drop in the condenser was assumed to be also 2 psia (13.4 kPa). The solar-side working fluid flow rate was 112,000 lbm/hr (50,909 kg/hr). Using the base design operating conditions given above, all the components for the cycle were fixed in size: the turbine, pumps, and heat exchangers. Using the fixed-size components, we carried out off-design tests to study the performance of the cycle. Among many elements that affect the performance of such cycle are the ambient air temperature variations and the flow rate of the solar-side working fluid. The first set of off-design studies was conducted by maintaining the ambient air temperature at 80°F (26.7°C) and varying the solar-side working fluid flow rate from full flow (100%, MH = 1) down to 35% (MH = 0.35) flow rate. Specifically we used 35%, 50%, and 75% flow rates and obtained cycle performance data. For each flow rate, the turbine inlet pressure was varied until a maximum efficiency point was obtained. Based on the load, the air flow rate was also adjusted to maintain a 5°F pinch inside the condensing unit. Figure 16 shows the results for this particular set. This figure shows that a straight line may be drawn through the maximum efficiency points. Table 9 gives the details for the maximum efficiency points for various solar-side fluid flow rates. 21

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