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1. Introduction Task 2 Wet/Dry Heat Rejection Analysis Task 2 Comparison of Wet and Dry Rankine Cycle Heat Rejection The efficiency of a Rankine cycle is defined, in large part, by the pressure and the temperature of the steam both entering and leaving the turbine. The cycle efficiency can be improved either by raising the pressure and the temperature at the inlet to the turbine, or decreasing the pressure and the temperature at the outlet. The steam conditions at the turbine outlet are defined by the temperature at which the steam is condensed and the latent heat of vaporization can be transferred to the environment. The lowest ambient temperature available is the wet bulb temperature; thus, most power plants use an evaporation process to provide the cooling water source for the condenser. However, the principal heat transfer mechanism in a wet cooling tower is evaporation. As a result, approximately 1 pound of water must be evaporated for each pound of steam condensed, and the water consumption in a large power plant can be significant. For example, an 80 MWe parabolic trough solar plant, operating with a capacity factor of 27 percent, will consume about 725,000 tons of water per year. For sites which have a limited supply of water, heat can be rejected to the environment by condensing turbine exhaust steam at the dry bulb, rather than the wet bulb, temperature. For desert sites, design values for the dry bulb and the wet bulb temperatures are about 104 °F and 68 °F, respectively. Compared with a turbine inlet temperature of 703 °F, a difference of 36 °F in the steam condensation temperature does not appear significant. However, the work performed in the turbine expansion process is defined as ∫ν dP, where ν is the fluid specific volume and dP is the change in pressure. With a turbine inlet pressure of 1,450 lbf/in2, and an outlet pressure of 1.07 lbf/in2 defined by a condensation temperature of 104 °F, a theoretical overall pressure ratio of 1,360 can be achieved. However, an outlet pressure of 0.34 lbf/in2, defined by a condensation temperature of 68 °F, results in an overall pressure ratio of 4,260. Granted, the theoretical pressure ratios cannot be achieved due to economic limits on heat exchange area. Nonetheless, it is clear that small changes in the condensation temperature can have a large influence on the expansion ratio, and therefore the work performed by the steam. An economic analysis was conducted to determine 1) the preferred design conditions for a dry cooling tower, and 2) the anticipated increase in the levelized cost of energy due the selection of a dry, rather than a wet, cooling tower. For the purposes of the analysis, the power plant was assumed to be an 80 MWe parabolic trough facility located near Barstow, California. The study was conducted through the following steps: • A model of an 80 MWe Rankine cycle using an air cooled condenser was developed using the GateCycle program (Reference 1). Six models were developed, with initial temperature differences between 24 °F and 49 °F. (Initial temperature difference is defined as Dry bulb temperature - Steam condensation temperature.) For each of the six models, estimates of turbine output and cooling fan power demand were made for dry bulb temperatures between 40 °F and 130 °F. -1-PDF Image | Nexant Parabolic Trough Solar Power Plant Systems Analysis
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