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The 4th International Symposium – Supercritical CO2 Power Cycles September 9-10, 2014, Pittsburg, Pennsylvania perform the compression in two stages thereby allowing the recuperated energy to be added between the two stages. This feature looks similar to compressor inter-cooling; however, recuperated heat is added to the intermediate pressure flow stream rather than being removed. For smaller SCO2 power cycles this has the added effect of increasing the volumetric flow rate through the compressors which lowers the compressor speed, allows for a larger compressor, and thus increases the compressor efficiency. The last major benefit is that it lowers the amount of heat that needs to be rejected to the environment because a large fraction is recuperated back into the loop. It therefore lowers the cost of the heat rejection hardware. 3. Cycle Switching from Non-Condensing Brayton to an ICE-condensing Rankine: The cycle uses valves to select the type of heat rejection (condensing/non-condensing). During off-peak demand times, the power production process uses a heat sink that is non-condensing with respect to the CO2. For this power cycle the heat can be rejected to water via an evaporative cooler or it can be rejected to air. This results in the compressor inlet being above the critical temperature which makes the power system an SCO2 Brayton cycle. However, valves can be used to switch the CO2 flow to an “Ice-on-Coils” bulk energy storage tank to melt the ice, and thus condense the CO2. Because the CO2 is cooled to +5C which is below the critical temperature (31 C), it therefore has a vapor pressure that is below the critical pressure resulting in CO2 condensation. This Ice-melting heat rejection process is part of the “discharge” power cycle. It melts the ice that was previously generated in a “charging” process during low demand (late evening and early morning) when excess renewable wind energy is often available. Also note that to accommodate the larger pressure ratio in the ICE-Rankine discharge cycle, both the turbine and the compressor will require an additional stage that must be valved in or out when switching between the Brayton and the Ice Rankine cycle (not shown in the figure). The thermodynamic cycle analysis presented in the process flow analysis was determined by using Microsoft Excel 2010 with the spreadsheet solver, and coupled to the NIST Refprop subroutines for the CO2 equation of state. The waste heat source was selected to represent the combustion gas flow (~69.8 kg/s at 538 C) from a 25 MWe class gas turbine or flue gas from manufacturing process with greater than 40 MWth of waste heat at a similar temperature. The process flow diagram is presented in Figure 1, while the results of the temperature and pressure state point analysis, plus the fluid flow rate and fluid type are provided in Table 1. A summary of the thermal or mechanical power in the heat exchanger and turbomachinery components is presented in Table 2. Likewise the T-S curves for both the Ice-Rankine and the Brayton cycles processes are illustrated in Figure 2(a & b). A summary of the expected performance for the off-peak Brayton cycle and the on-peak Ice-Rankine cycle is provided in Table 2. The CO2 mass flow rate through the discharging Ice-Rankine cycle was selected to reject all of the CO2 waste heat by melting the ice over a 4 hour period. The refrigeration system size was selected to provide sufficient ice for these four hours of heat rejection (ice-melting), but was generated during an 8 hour period during the late evening and early morning hours. Two types of refrigeration systems were assumed for the analysis. One uses an expansion valve. The other uses a turbo-expander to recover some of the expansion energy. These cycles are described in the next section.PDF Image | Bulk Energy Storage using a Supercritical CO2 Waste Heat Recovery Power Plant
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