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64 equation(β3-4), is assumed to be 65% and is considered a realistic value for reducing the impact on the total ORC performance. As πππ’ππ decreases, the amount of power consumed by the pump increases, which results in low cycle efficiency. The pump inlet conditions are the same as the condenser outlet conditions. The pump outlet conditions can be obtained through the known isentropic efficiency and the pump power. Assuming an isentropic compression through the pump, the required pump power can be calculated using equation (β3-5). πππ’ππ = ππ ,π€π ,ππ’π‘ β ππ€π ,ππ (β3-4) ππ€π,ππ’π‘ βππ€π,ππ π = ππ€π ππ ,π€π ,ππ’π‘ β ππ€π ,ππ (β3-5) ππ’ππ πππ’ππ ππππ‘ππ 3.3.5 Turbine Modelling Expander modelling considers the turbine volute, stator and rotor. Given that volute is responsible for the turning of the fluid, the stator vanes aim to accelerate the flow and deliver it to the rotor inlet uniformly and at the correct angle. An isentropic efficiency is assumed at the beginning. Then, the actual enthalpy drop on the rotor, stator and volute are calculated. Once the losses are calculated, the new isentropic efficiency is calculated. The loop ends when the estimated and calculated isentropic efficiencies converge. The turbine power output of the turbine expander is calculated using equation (β3-6). The turbine model is detailed in βChapter 5. π = π π (π β π ) π‘π’πππππ π‘π π€π 5 6,ππ 3.3.6 Integrated Heavy-Duty Diesel Engine (β3-6) The design of the ORC system is based on the exhaust heat flow of a 7.25 L Yuchai engine. This HDD engine is turbocharged, direct injection and fulfils EURO III regulatory constraints. Theengine is tested at Brunel UniversityPDF Image | Automotive Radial Turbine Expander Design WHR
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