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Chapter 5 if compared to the layout given in Fig. 5.1. Therefore, only one ORC unit is considered as the bot- toming unit for gas turbine A. Due to the relatively low temperature of the gas turbine exhaust (see Tab. 5.1), its thermal energy can be transferred directly to the ORC unit through the once-through boiler (OTB), without the need of an intermediate oil loop. Thus, the working fluid is first expanded in the ORC turbine (TUR), and subsequently cooled down in the recuperator. In this way the inlet temperature in the OTB may be increased by recovering energy from the superheated vapor exiting the turbine. The ORC fluid is then condensed and pumped up to the highest pressure level through the recuperator, thus closing the cycle. Based on the analysis performed in Ref. [10], the selected ORC working fluid is cyclopentane. This compound is already adopted for operating ORC systems in this range of temperature, see Ref. [12]. For the steady state calculations, thermodynamic and transport properties of cyclopentane are calculated according to the model implemented in a well- known program [13]. The same thermodynamic library is linked to the dynamic modeling tool by means of a specific interface for the Modelica language [14], and to the general interface to fluid property libraries Fluidprop [15]. It is assumed that in the new power generation system the base-load power demand (19 MWE) is shared between the combined cycle (gas turbine A and ORC) and one gas turbine, while the other engine is on stand-by. As a net power output up to 6.4 MWE can be harvested by the ORC turbo-generator, the load is split so that the combined cycle provides 13 MWE and the remaining 6 MWE are supplied by gas turbine B [10]. Note that the combined cycle alone could potentially cover the entire base-load power demand with a higher efficiency; however, this option is discarded since the necessary reserve power for peak loads would not be immediately available during normal operation, as it would require the ignition of one of the gas turbines. Moreover, the proposed configuration allows to stop the combined cycle for maintenance by running gas turbine B and C, each supplying 50% of the load. 5.4 System Modeling 5.4.1 Preliminary ORC Power Plant Design As described in §5.2.1, the design procedure starts with the calculation of the thermodynamic states of the working fluid at the inlet/outlet of each component, see Fig. 5.1, by solving mass and energy balances, complemented by constitutive equations; the details of the non-linear system of equations can be found in Ref. [10]. At this stage, the gas turbine is modeled as a lumped thermal source, whose output constitutes the main input for the ORC turbo-generator design optimization. The characteristics assumed for the gas turbine exhaust stream are reported in Tab. 5.1. Figure 5.2 illustrates the T–s diagrams of two ORC power unit candidates obtained via the multi-objective optimization approach described in §5.5.1, while the results of the thermodynamic states calculation are listed, for one such candidate designs, in table 5.2. HEAT EXCHANGERS The heat exchange equipment is designed following the well-established standard procedure de- tailed in Ref. [16]. Compared to the work carried out in the previous work by Pierobon and colleagues [10], a new model of a once-through boiler has been developed and implemented. More- over, since finned tubes have been foreseen in order to enhance the heat transfer process, specific correlations are utilized to evaluate the heat transfer coefficients and the pressure drops outside the tubes. 126PDF Image | New Concepts FOR Organic Rankine Cycle Power Systems
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