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Based on the parameters presented above, the IPSEpro PSE models of a dual heat source ORC system were developed using the following design constraints: • The pinch point temperature difference in the heat exchangers is assumed to be equal to 2oC. • The condenser is water cooled with a source temperature of 7.6oC. • The working fluid is at the saturated vapour state at the entrance to the turbine. • To avoid persistent fouling of the evaporator’s surface (which adds to the cleaning cost) which might occur as a result of condensation of oil contained in the effluent waste streams, the waste heat must leave the evaporator as saturated vapour after being used to preheat and evaporate the working fluid. • The pressure at the inlet to the turbine is set to achieve optimum power output and thermal efficiency from the ORC system while maintaining the design constraints. 6.3.1 Proposed Water Cooled Dual Heat Source ORC System The IPSEpro PSE model of the proposed dual heat source ORC system using water as the condenser cooling fluid is shown in Figure 6-3 . The T-Q diagram of the preheater 2/evaporator, de-superheater/condenser and the T-s diagram of R245fa working fluid at design point are shown in Figures 6-4, 6-5 and 6-6 respectively. The thermodynamic processes exhibited by the working fluid are shown in Table 6-2. 125PDF Image | OPTIMISING THERMAL ENERGY RECOVERY
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