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28 • Second Law efficiency, which is the ratio of work done by the power cycle to the theoretical maximum amount of work [Moran & Shapiro, 2002]: η Where Ψ is the specific availability of the HTF and is defined as (neglecting kinetic and potential energy effects): Ψx =(hx −h0)−T0(sx −s0) [3.1.14] • Component Availability Destruction (steady-state, adiabatic), which is the 2ndlaw = ηgeneratorWturbine −Wpump [3.1.13] m&HTF,in(ΨHTF,in −ΨHTF,out) resource availability that was not successfully converted into useful work: A = m& Ψ − m& Ψ − A &∑∑& 3.1.1 Alternate cycle configurations [ 3 . 1 . 1 5 ] destruction in in out out work The model presented in the preceding section is specifically formulated for the reference cycle. The unique modeling details of each alternative configurations of interest are discussed below: Reference cycle without recuperation No modifications to the model are required to accommodate this change, the effectiveness of the recuperator is simply set to zero. Reference cycle with turbine reheat In this cycle two turbine stages are used. The working fluid is expanded to an intermediate pressure, reheated, and then extracted to the condensing pressure. The intermediate pressure is a design parameter. Figure 3.8 shows a schematic of such a system. &&PDF Image | Organic Rankine Cycle Solar-Thermal Powerplants
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