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4.1.4 Boiler module For the purpose of modelling, a heat source consisting of hot water at a temperature of 100°C characterized by a flow rate of 10 kg/s, heat sink assumed to be cold water with supply temperature of 25°C and R245fa as a working fluid is considered. As heat losses in heat exchangers are neglected, the amount of the heat added to the working fluid in time is equal to the heat extracted from the heat source. In the modelled preheater, specific heat capacity is considered constant allowing the log mean temperature difference technique to be employed (figure 36). Figure 36 Temperature change of working fluid and waste heat source along the heat exchanger length (assumption for LMTD) Due to the uncertainty in measuring two phase fluid properties at the expander inlet, it’s important to approximate the dryness fraction at the inlet numerically. Therefore, the total heat transferred from the waste heat source is balance between preheater and evaporator such that when taking the expander efficiency into account the expander inlet conditions are such that the expander exit dryness will be X=0.99. In doing so, taking heat exchanger pressure drop into account the organic fluids condition at the heat exchanger exit can be calculated and the temperature profile can be found (figure 38). In brief, an energy balance on the boiler heats the working fluid at the pump outlet to the expander inlet condition. The waste heat source is divided into 0.01°C increments in order to find the optimised cycle so that the working fluid dryness fraction at the expander exit is limited to X=0.99. 56PDF Image | study of ORC with the expansion process twin screw machines
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