Analysis of optimization in an OTEC plant using ORC

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Analysis of optimization in an OTEC plant using ORC ( analysis-optimization-an-otec-plant-using-orc )

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hth 1⁄4 Wnet (16) Qeva Finally, the objective parameter that represents the ratio of net power output, Wnet, to total heat transfer area, A, in the system is defined as g 1⁄4 Wnet (17) At 4. Results and discussion 4.1. Problem description A finite-temperature-difference heat transfer method, which means heat transfer occurred only with temperature difference between seawater and working fluid, is applied to evaluate the heat transfer area of the condenser and evaporator in an OTEC system with an ORC. R134a, R152a, R245fa, R600a, and R717 are used as the working fluids. In this study, the warm seawater flow rate remains fixed, the mass flow rate of working fluid varies to obtained the optimal temperature conditions. This section presents the results of parametric studies on the various working fluids in the system. The following general assumptions were made in thermodynamic analysis: 1. Steady-state conditions are applied to all components. 2. Warm seawater flow rate: 2000 kg/s. 3. Evaporation temperature: 18e24 C. 4. Condensation temperature: 8e14 C. 5. Cold seawater temperature: 5 C. 6. Warm seawater temperature: 28 C. 7. Seawater temperature differences between inlet and outlet are the same in the evaporator and the condenser. 8. Efficiencies of cold and warm seawater pumps and working fluid pump: 0.8. 9. Turbine efficiency: 0.9. 10. Condenser and evaporator are shell-and-tube heat ex- changers and the correction factor F is 0.9. The thermodynamic data used in this analysis are obtained from the National Institute of Standards and Technology (NIST) database REFPROP 9.0 [24]. 4.2. Verification To evaluate the accuracy of the power output calculation for the OTEC system, the numerical solution of net power output in the ORC system is verified using the results of Sun et al. [10]. The re- lationships between net power output and various mass flow rates of warm seawater are compared using R717 as the working fluid with Teva 1⁄4 22.2 C and Tcon 1⁄4 10.8 C. The cold and warm seawater inlet temperatures are assumed to be 5 C and 28 C, respectively, for the simulation. However, the power consumptions of cold and warm seawater pumps were not included in evaluating system power output, Wver, for verification. Overall comparison shows that the numerical solutions of this study agree well with those of Sun et al. [10], as shown in Fig. 3. 4.3. Performance optimization Fig. 4(a)e(c) plot the influence of evaporation temperature on net power output, total heat transfer area, and the objective Fig. 5. Dependence of (a) Wnet, (b) At, and (c) g on condensation temperatures at Teva 1⁄4 22.3 C and DTw 1⁄4 2.1 C. M.-H. Yang, R.-H. Yeh / Renewable Energy 68 (2014) 25e34 29

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