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desirable for large area requirements because of their large surface-area to volume ratio. Therefore, the compact plate heat exchanger architecture was chosen to reduce the overall size of the heat exchanger. The MATLAB code in section 3.2 was modified to arrive at a new area requirement using the plate convection correlation, h [28] given by Eqn. (18). 0.374k Re0.668Pr0.33 h D (18) h Due to the operating pressures and temperatures aluminum and copper heat transfer interfaces were not viable. The high side temperature is in the aging range of aluminum, which leads to eventual embrittlement and weakening below an acceptable level. Copper has acceptable temperature performance, but was not viable due to its low material strength. Therefore, stainless steel was selected because it provided the best compromise between strength and thermal conductivity at the operating pressure and temperature. Plate thickness was determined by calculating σmax. [34] via the relationship of Eqn. (19). 0.3078wb 2 max t2 (19) The overall heat transfer coefficient was then corrected for conduction through the wall. The stainless steel thickness had little effect on the overall heat transfer coefficient because the thermal choke occurs in convection between the wall and the fluid core. 5. Conclusions The above analysis examines the feasibility of a regenerative Rankine cycle utilizing SCO2 for waste heat recovery in small-scale systems. Initial analysis suggests that recovery from low temperature sources approximately 200°C and above is feasible with an operating efficiency of 11% given the conservative operating parameters in Table 1. Agreement between the present results and those of [11-13,15,16] has been demonstrated offering validity to the current study. Further analysis and experimental validation is required for optimal development of hardware that may be used for low flow rates. It is notable that the overall thermodynamic efficiency of the system is highly dependent on the internal heat exchanger effectiveness and it is expected that higher system efficiencies may be achieved after development and optimization of the system. References [1] U.S. Energy Information Administration Office of Integrated Analysis and Forecasting. Annual Energy Outlook 2010, US Department of Energy, 2010. [2] Waste Heat Recovery in Industrial Facilities: Opportunities for Combined Heat and Power and Industrial Heat Pumps. EPRI,Palo Alto, CA: 2010. [3] Waste Heat Recovery: Technology and Opportunities in U.S. Industry, BCS Incorporated, Report to U.S. DOE Industrial Technologies Program, March 2008. [4] An Inventory of Industrial Waste Heat and Opportunities for Thermally Activated Technologies, Report for Oak Ridge National Laboratory, United Technologies Research Center, 2004. [5] V. Dostal, M.J. Driscoll, P. Hejzlar, “A Supercritical Carbon Dioxide Cycle For Next Generation Nuclear Reactors”, Massachusetts Institute of Technology, Dept. of Nuclear Engineering, 2004. [6] X.R. Zhang, H. Yamaguchi, K. Fujima, M. Enomoto, N. Sawanda, “Experimental Performance Analysis of Supercritical CO2 Thermodynamics Cycle Powered by Solar Energy, Flow Dynamics”, The Second International Conference on Flow Dynamics, 2006. [7] J. Sarkar, S. Bhattacharyya, “Optimization of Recompression SCO2 Power Cycle with Reheating, Energy Conversion and Management”, Elsevier, 2009. [8] J. Sarkar, “Second Law Analysis of SCO2 Recompression Brayton Cycle”, Energy, Elsevier, 2009. [9] S. Wright, R. Radel, M. Vernon, G. Rochau, P. Pickard, “Operation and Analysis of a SCO2 Brayton Cycle”, Sandia Report, Sandia National Laboratories, 2010. [10] E.W. Lemmon, M.L. Huber, M.O. McLinden, “NIST Standard Reference Database 23: Reference Fluid Thermodynamic and Transport Properties-REFPROP”, National Institute of 8PDF Image | Waste Heat Energy Supercritical Carbon Dioxide Recovery Cycle Analysis and Design
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