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Energies 2022, 15, 6398 11 of 23 - - - - - ated with the central heating system is disbursed for radiator technology (70/50 ◦C in existing facilities and 50/35 ◦C in new facilities). Similarly for mechanical ventilation, where it is assumed that the small heat flux for air curtains is included in the mechanical ventilation flux of 70/50 ◦C, as in the existing facilities (in favor of certainty). In the newly constructed facilities, 60/40 ◦C has been assumed for ventilation. Hot water heating up to 60 ◦C was assumed (in order to ensure the required 55 ◦C in water intakes, assuming possible transmission losses). The temperature was assumed to be raised by 2 K in the pool exchangers responsible for maintaining the water temperature during the normal operation of the facility. A water temperature of 10 ◦C was assumed in the water supply system. The following parameters for the geothermal water extracted from the planned Cho- chołów GT-1 borehole were assumed for the analysis: • Temperature 88 ◦C; • Pressure 160 kPa; • Flow capacity 160 m3/h (equivalent to a mass flow of 44.44 kg/s). 3.2. Description of the Process Line The process diagram of the proposed installation is shown in Figure 5. The capacities in the diagram refer to the differences in enthalpies between the inlet and the outlet (an isobaric heat exchange was assumed). For the thermal water intake and discharge, the values have been referred, using a temperature of 0 ◦C. Geothermal water with a temperature of 88 ◦C and a pressure of 1600 kPa, moving at a rate of 160 m3/h will be drawn from the source. Its potential is 16,436.5 kW of heat when the water is cooled to 0 ◦C. Assuming that the water injected back into the ground will be 12.8 ◦C, the maximum heat output to be received from the geothermal water will, therefore, be 16,436.5 kW − 2395.6 kW ≈ 14 MW. The first step in the process line is the installation of an ORC evaporator, which lowers the feed temperature of the first of the heat exchangers (from 88 ◦C to 78 ◦C) and, consequently, limits the high-parameter heating power available in the system. However, the location of the evaporator results from the nature of the thermodynamic transformation of the low-boiling medium, so that, to maintain at least a satisfactory level of electrical power in the system, relocating it within another heat exchanger was not considered (this would have required, among other things, the provision of an additional heat source, preferably with a temperature above 100–120 ◦C). Due to the relatively low evaporation temperature of the R134a refrigerant in the ORC line, the heat from the evaporator is usually exported to the atmosphere, e.g., in a fan cooler. In the case of the facility under study, however, it is possible to use some of this heat (134.1 kW), e.g., to maintain the water temperature in pool B15. The ORC circuit, however, primarily yields 221.4 kW of net electrical power. Then, downstream of the ORC circuit, the geothermal water flows through a water turbine to utilize the available pressure; the drop in pressure to 250 kPa allows 48.3 kW of net electrical power to be generated. The turbine is an example of a system for active pressure reduction, allowing the pressure to be adapted to the conditions in the heat exchangers, with energy recovery (unlike valves and other passive systems). The proposed microturbine is of a Francis type, with an expected efficiency of 86% and a speed rate of 750 r/min. Another element of the process line is the heat exchanger plant, consisting of six suc- cessive heating stages and one geothermal water vent. The heating stages are a series of cascade (series)-located heat exchangers, further reducing the temperature of the geother- mal water and cooperating with the appropriate heating circuits with adapted parameters (temperature ranges).PDF Image | Combined Renewable Energy Resources System Geothermal
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