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Ing. Patrick Schwarzbauer Solar thermal organic Rankine cycle (ORC) discuss the plausibility of an ORC for small scale applications, like public housing. Some applications for Organic-Rankine cycle are [4]: • Biomass combined heat and power • Geothermal energy • Solar power plants • Waste heat recovery However, this research paper focuses on solar thermal applications only. The ORC cycle is shown in Figure 7. Solar radiation (1000 W/m2) heats up a heat transfer fluid (100-200°C), in this specific case the working fluid is R134a. The fluid than passes a heat exchanger, where the earned heat can be transferred to the ORC. This heat exchanger is called vaporizer or evaporator. The heat transfer fluid will be pumped back to the solar panels and the process starts again. The working fluid (organic fluid) of the ORC evaporates passing the vaporizer. The gas should be superheated to avoid erosion in the turbine. Heat energy can be converted into technical work and then into electricity. The turbine expands the working fluid isentropic (ideal) and begins to rotate. The rotation of the turbine drives a generator to produce electricity. The working fluid leaves the turbine with lower pressure. Afterwards the fluid will be condensed in a heat exchanger (e.g. air-cooled condenser, plate heat exchanger, tube heat exchanger). The liquid working fluid of the ORC will be pumped back to the vaporizer, and the cycle continues. There is also a type of system where the working fluid will be directly evaporated and superheated by passing the solar collectors. The unique part of this thesis is, that the turbine is a standard scroll compressor which is modified to act like a turbine. Bitzer, a German compressor manufacturer, is very interested in this project and donated the compressor for research purposes. The gas expands from a high-pressure level to a low-pressure level. As mentioned before, it is important that the gas at the exit of the turbine is still superheated or directly on the saturated vapor line. The quality of the steam “x” shouldn`t be less than one (x=1) to protect the turbine from erosion caused by liquid drops in the gas. The high velocity of the gas- liquid mixture will lead to major damage of the turbine. Both heat exchangers, evaporator and condenser, consists of two or three phase evaporation and condensation of the working fluid. The number of phases in each heat exchanger depends on following aspects: • superheated or saturated gas (x=1) at the inlet of the condenser • supercooled or saturated liquid (x=0) at the exit of the condenser • supercooled or saturated liquid (x=0) at the inlet of the evaporator The heat capacity of the superheated gas is low in comparison to the capacity of the saturated gas. This can be easily calculated by multiplying the mass flow rate with the enthalpy difference of each phase. For designing such systems, logp-h diagrams are very helpful. Capacities for evaporation and condensations can be calculated quickly by using such diagrams. The liquefied refrigerant exiting the condenser will be collected in a liquid refrigerant collector, for schematic symbols and drawings see Figure 3 and Figure 7. Figure 7. Schematic drawing of the ORC cycle. The thermodynamic cycle is shown in Figure 8 and Figure 9. Both diagrams are generated with an Engineering Equation Solver (EES). This software contains all important thermophysical properties of all kind of fluids as well as thermodynamic equations for solving difficult applications. After programming the code, it is easy to change values like temperatures and mass flow rates to analyze the system. Figure 8. T-s diagram of the ORC cycle. Figure 9. Logp-h diagram of the ORC cycle. -4-PDF Image | Solar thermal organic Rankine cycle (ORC)
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