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3-2 System Model 19 Figure 3-3: An illustration of the Sankey diagram of a diesel engine (Energy flow not to scale) and in the EGR system are taken from accurately measured engine maps [21] and have been reported in Table 3-3. Pressure drops of 5kPa and 0.5kPa are assumed in the working fluid side and flue gas side of the heat exchangers respectively based on the heuristic knowledge that plate type heat exchangers have low pressure drops. Figure 3-4: System Layout of ORC turbogenerator for automotive heat recovery [8] A 5 K of superheating with respect to the temperature at the corresponding evaporation pressure has been specified to ensure that no liquid droplet can enter the turbine [21]. A high speed turbine has been implemented because of its advantages over piston and scroll expanders described previously in section 2-4, the details of which are described in the following sections. A regenerator is used to recover heat from the vapor leaving the turbine to preheat the fluid entering the evaporator. Constraints on the heat exchanger pinch point have been considered which are discussed later in section 3-4. The condenser is also bound by the cooling water flow rate in addition to the volumetric flow rate from the turbine outlet. The amount of head available for the cooling water circulation pump in a truck is limited. Hence, this pump has Master of Science Thesis Akshay HattiangadiPDF Image | Working Fluid Design for Organic Rankine Cycle
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