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Figure 5: Three commonly used reflecting schemes for concentrating solar energy to attain high temperatures A Fresnel lens concentrator uses refraction rather than reflection to concentrate the solar energy incident on the lens surface to a point. These lenses are used in photovoltaic concentrators. [4] 5. CONCEPT DESIGN G = Ta = Tm = A = solar irradiation [W/m2] ambient air temperature [°C] collector mean temperature [°C] collector area (corresponding to the Using these parameters, the collector efficiency can be A theoretical model of the Rankine cycle based on low expressed: temperature solar thermal heat has been developed. This is shown in Figure 5 below. Figure 6: Concept design of a low temperature solar thermal conversion power plant The system consists of two cycles: a solar thermal cycle and a rankine cycle, with a heat exchanger providing the interface. Currently, mathematical modeling of the system is being undertaken. This will be followed by experimental research to determine correlation of the theoretical model. For this purpose a 10 kilowatt IT10 Vapour Turbine from Infinity Turbine is being sourced. This, therefore, forms the basis for detail design of both the rankine cycle as well as the solar thermal cycle. 5.1 SOLAR THERMAL CYCLE DESIGN The main components on this cycle are the solar collectors, the pump and the heat exchanger. These are connected by insulated ducting. Solar collector design entails selecting an appropriate type of collector, in this case flat plate collectors, and sizing. n = n0 – a1(Tm-Ta)/G – a2(Tm-Ta)2/G [2] The design for the heat exchanger, pump and ducting will be based on the design thermal loading resulting from the Rankine cycle as well as the solar collectors. The type of heat exchanger selected for this application is the shell and tube heat exchanger in the countercurrent flow configuration. The overall governing equation for shell and tube heat exchangers is: QT = UAF(LMTD) [3] where: QT is the total heat load to be transferred U is the overall heat transfer coefficient referred to area A A is any convenient heat transfer area F is the temperature correction factor LMTD is the logarithmic mean temperature difference for the purely countercurrent flow configuration. This equation is supported by the two heat transfer equations for the hot and cold fluids thus: QH = mH CPH (TinH – ToutH) [4] QC = mC CPC (ToutC – TinC) [5] where: Q = heat transferred in joules per unit time m = mass flow rate T = temperature CP = specific heat capacity of fluid Subscript ‘H’ = hot fluid Subscript ‘C’ = cold fluid [5] Sizing of flat plate collectors is based on European Standards EN12975 parts 1 and 2 (or on equivalent SABS standards). The heat transfer fluid is water mixed with antifreeze. Thus, the power from the solar collector may be determined by the equation: P = A*(n0*G – a1*(Tm-Ta) – a2*(Tm-Ta)2) [W] [1] where: n0 = a1 = a2 = Zero-loss efficiency 1st order heat loss coefficient 2nd order heat loss coefficient efficiency parameters) [m2]PDF Image | LOW TEMPERATURE SOLAR THERMAL ENERGY
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