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2. Methodology and assumptions 2.1. System description For the numerical simulations performed in the study, a generic heat source stream consisting of dry atmospheric air is assumed. The saturated liquid refrigerant is pressurized with a pump. A heat exchanger is used for transferring the energy content of the heat source to the working fluid. Due to the relatively low heat source temperatures considered in the present study, the heat exchange between the waste heat stream and the working fluid takes place directly, without the integration of an intermediate heat transfer loop, which is a fairly common practice in WHR applications. Depending on the maximum operational pressure of the cycle, the working medium is introduced to the expander either as saturated vapour or at supercritical state. No superheating is deemed necessary for the fluids investigated (except for Propane), since the slope of the saturation curve in the T-S diagram has a negative value (dry fluids) and therefore no liquid phase occurs at the expander outlet. 2 QORC,in Heat exchanger 1 Pump Expander Generator G Pel • QORC,out Cooling 4 water • HSin HSout 3 P m (hh) exp ORC 2 3 (1) Condenser Cwin Cwout Fig. 1. Schematic process scheme of the WHR-ORC investigated Following the expansion process, the superheated fluid stream flows through the condenser, where it is cooled down by a stream of cooling water. The condensed saturated liquid re-enters the pump, repeating the cycle (Fig. 1). The simulations of the thermodynamic cycle and the calculations of all thermophysical properties were carried out using the AspenPlusTM software by using the Peng-Robinson equation of state with Boston-Mathias alpha function property method [27]. A steady state operation is assumed, while the heat and pressure losses through piping, fittings and heat exchangers are considered equal to zero. 2.2. Performance evaluation parameters During the expansion process of the working medium, an amount of power Pexp is produced in the turbine. The mechanical efficiency ηm is used to represent the percentage of Pexp that is lost due to friction losses in the shaft and the gearbox that connect the expander with the rotor of the electric generator. Additional power losses occur during the conversion of the mechanical power of the shaft to electricity in the generator. These losses are indicated by the generator efficiency ηG.The gross electricity produced by the WHR-ORC is thus given by the equation: 5PDF Image | Thermodynamic investigation of waste heat recovery
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