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Hanzhi Wang et al. / Energy Procedia 105 (2017) 1889 – 1894 1891 where Wpump is the power consumed by the pump; h4s is the isentropic specific enthalpy of working fluid at the pump exit; ηpump is the pump isentropic efficiency; Wtur is the turbine power output; h2s is the isentropic specific enthalpy of working fluid at the turbine exit; ηtur is the turbine isentropic efficiency. The first and second law efficiencies of the ORC (ηI and ηII) are defined by Eqs. (5) and (6) I Wnet Qin (5) W Q 1-T T (6) II net in 0m where T0 is the ambient temperature; Tm is the mean heat source temperature; Qin is the heat transfer rate in the evaporator. The turbine size factor (TSF), which is proportional to actual turbine size [14], is defined by Eq. (7) TSF V H1/4 (7) 2 is where V2 is volumetric flow rate at turbine exit, and ΔHis is the isentropic enthalpy difference in the turbine. 3. Results and discussion The purpose of this study is to parametrically analyze and compare the net power output, efficiency and turbine size factor of the ORCs using HFE7000, HFE7100 and HFE7500 as working fluids. A computer program in Engineering Equation Solver (EES) has been developed to simulate the thermodynamic performance of the tested working fluids under various turbine entry temperatures (TET). As previous researches such as [15-16] indicate that no superheating is preferred for dry fluids in the ORCs, the condition of the fluid at the turbine inlet is set to the state of saturated vapour in this study. In the following analysis, the input parameters are set as follows: the heat source mass flow rate is 1.0 kg/s; the heat source temperature is 150 oC; the condensing temperature is 28 oC; the turbine and pump isentropic efficiencies are 0.80 [17]; the pinch temperature differences in the evaporator and condenser are assumed to be 5 oC; the ambient temperature is 298 K. These input parameters keep constant for all cases. The analysis is provided graphically in Figs. 2-5. Fig. 2 shows the effect of the turbine entry temperature on the net power output of the ORC. It is found that with different working fluids, the influences of the TET on the net power output are similar. The net power outputs of HFE7000, HFE7100 and HFE7500 increase with the TET firstly but then decreased, and there exists optimum TET values that can maximize net power outputs. Among these three working fluids, HFE7000 has the lowest boiling temperature. Generally the working fluid of low boiling temperature produces large net power output. However, HFE7000 and HFE7100 produce almost the same net power output in the low TET, and this is because under the set conditions the mass flow rate of the working fluid is different. Actually, HFE7100 and HFE7500 obtain higher mass flow rates under the same TET. Fig. 3 presents the effect of TET on the first law efficiency of the ORC. It shows that the first law thermal efficiency increases monotonically with the TET. With the TET rising from 340 to 385 K, the first law efficiencies approximately increase from 7.76% to 12.58% for HFE7000, from 7.55% to 12.09% for HFE7100, and from 7.54% to 11.95% for HFE7500. HFE7000 obtains the highest thermal efficiency, followed by HFE7100, and HFE7500 which shows relatively poor performance. The variation of second law efficiency versus the TET is shown in Fig. 4. It can be seen that the second law efficiencies increase with the TET but the slope of the curves decreases. This is coordinate with the research done by Liu et al. [18]. In the present study, HFE7000 performs better than other two working fluids on the second law efficiency especially under higher TET. In Fig. 4, the second law efficiencies increase 12.91% for the HFE7000, 10.89% for the HFE7100 and 10.92% for the HFE7500.PDF Image | Thermodynamic Analysis ORC Hydrofluoroethers working fluid
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