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Kalina cycle using ammonia/water mixtures as working fluid, and two-tier ORC proposed by Reflective Energies. NREL’s analysis of the ORC cycles are presented in the following sections. The analysis of Exergy (Appendix A) for their proposed Kalina cycle and the two-tier cycle proposed by Reflective Energies are presented in the appendices. Our analysis of potential ORC configurations was conducted using the commercially available thermal-process modeling software (from Aspen Technology, Inc.) These cycles and their corresponding performance information are listed in Table 1. 3.2.1 Basic ORC with Pure Hydrocarbons The basic ORC analyzed in this work is shown in Figure 1. The resource entered the heat exchanger at 580°F (304°C), and its exit temperature was 181°F (82.7°C). The working fluid, Pentane, was pumped from a pressure of 20 psia (0.138 MPa) at 114°F (45.6°C) (saturated liquid conditions) to a pressure of 610 psia (4.2 MPa). The working fluid was then passed through the main heat exchanger, where it was heated and boiled by the oil from the solar field to a temperature of 563°F (295°C). The vapor exiting the boiler at 600 psia (4.14 MPa) (a pressure drop of 10 psia was assumed for the boiler) was then passed through a turbine and was allowed to expand to 24 psia (0.165 MPa). The stream exiting the turbine was sent through an air-cooled condenser, where the working fluid was completely condensed. The efficiency of this cycle, including the fan power for the air cooler and the pump power, is 12.5%. A total pressure drop of 2 psia (13.8 kPa) was assumed for the air-cooled condenser. The heating and cooling curves for this cycle are presented in Figures 2 and 3. Figure 3 shows the source of inefficiency of this cycle. The vapor leaving the turbine is at a very high temperature of 433°F (223°C). In this case, the turbine exhaust is directly sent through a condenser with no attempt to recuperate any heat from this stream. Therefore, a significant amount of heat transferred to the working fluid from solar field is being rejected with no utilization. Our analysis in the next section will take advantage of recuperating heat from the stream exiting the turbine. The schematic of this cycle using software from Aspen Technology, Inc., is shown in Figure 4, and the state points corresponding to this cycle have been listed in Table 2. Note that a conservative condensing pressure of 20 psia was chosen for this analysis. It is possible to condense this working fluid at pressures as low as 15 psia; however, an above-atmospheric condensing pressure is very desirable for this cycle. 7PDF Image | Modular Trough Power Plant Cycle and Systems Analysis
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