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4 Advances in Mechanical Engineering Table2. Evaporatorperformanceparameters. Parameter (unit) Value Heat transfer area (m2) 9.5 Shell pass (mm) 2000 Inner diameter of shell (mm) 400 Pipe diameter (mm) 19 Number of pipes 73 Table3. Workingfluidpumpperformanceparameters. Parameter (unit) Value Flow rate (L/h) 3200 Head (MPa) 2.3 Motor power (kW) 7.5 Rated voltage (V) 380 Frequency (Hz) 50 ORC power generation technology for medium- and high-temperature waste heat sources (.150°C) is mature. For low-temperature heat sources, the effi- ciency of ORC power generation systems has to be improved.28–31 The preheater and superheater adopt plate heat exchangers, and the evaporator and conden- ser adopt full liquid types. The specific parameters of the evaporator are shown in Table 2. From the com- parisons made before and after installation, it is found that the installation of preheaters and superheaters can improve the system efficiency, and the installation of superheaters can further protect the turbine from the liquid impact phenomenon. When the evaporation temperature is 120°C and the condensation temperature is 35°C, the pressure drop in the working medium reaches the maximum value of 1.72MPa. JMD series hydraulic diaphragm pump of Nanfang Pump Co., Ltd. is selected as the working fluid pump. The specific parameters of the working fluid pump are shown in Table 3. The ideal ORC consists of four main thermody- namic processes (Figure 4): constant-pressure heating (6s–1), isentropic expansion (1–2s), constant-pressure condensation (2s–5), and isentropic compression (5– 6s). Owing to the resistance loss during expansion and compression, the actual expansion and compression processes are not isentropic. In Figure 4, points 1–2 indicate the actual expansion process for the working fluid in the expander, and points 2–4 indicate the heat- release process for the working fluid in the condenser. To ensure that the working fluid entering the pump is in the liquid state and to avoid cavitations, the super- cooling process 4–5 is added. The points 5–6 represent the pressurisation process of the working fluid, 6–7 the Figure 4. T–S diagram of ORC power generation system. preheating process, 7–8 the evaporation process, and 8–1 the superheating process. Superheated organic steam enters the expander to continue the following cycle. In addition, 9–12 and 13–16 represent the change trends in the heat source and cold source before and after the heat exchange. Figure 5 shows the schematic diagram of the ORC power generation system. The pressure loss of the ORC system is calculated and the simulation is performed to reduce the power consumption of the circulating water pump and working fluid pump, as shown in Figure 6. Boiler steam is used to replace industrial waste heat as the heat source of the system. The heat source used is saturated steam with pressure above 0.45MPa and a flow rate higher than 980kg/h. Figure 7 shows the photo of the ORC power generation system. The ideal expansion process in the expander is the isentropic expansion; however, there is irreversible loss in the actual expansion process. For this purpose, isen- tropic efficiency is defined as equation (1) h2 h1 ht=h h 3100% ð1Þ 2s 1 where h1, h2 and h2s are the enthalpies of inlet, outlet and isentropic expansion outlet of the turbine, respec- tively, in kJ/kg. In the actual expansion process, the isentropic efficiency will change with pressure, tempera- ture and other parameters. In the ORC system, the change in this value is small and can be regarded approximately as an invariant. The actual expansion power Ws can be calculated by equation (2) Ws = mf (h2 h1) = mf ht(h2s h1) ð2Þ where mf is the organic fluid mass flow rate (kg/s).PDF Image | ORC analysis of radial inflow turbine and R245fa
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