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TA 4.R: Supercritical Carbon Dioxide Brayton Cycle small size because of the low turbine pressure ratio and the high density of the working fluid, but this will be partially offset by the much higher mass flow rates required and the corrosion properties of high pressure CO2. R&D will be required on seals, bearings, and materials, particularly in applications having elevated turbine inlet temperatures. R&D will also be needed to develop low cost heat exchangers that are able to attain large heat transfer duties with small temperature differences between the hot and cold sides of the exchanger and with a small pressure drop. This will require R&D into compact heat exchanger designs, assessment of materials for suitability given the temperatures and pressures required, and advances in manufacturing techniques. Brayton Cycles based on CO2 as the working fluid Power cycles using sCO2 as the working fluid take on two primary configurations relevant to power generation: 1) an indirect-fired closed Brayton cycle that is applicable to advanced fossil fuel combustion, nuclear, and solar applications; and 2) a semi-closed, direct-fired, oxy-fuel Brayton cycle well-suited to fossil fuel oxy-combustion applications with CO2 capture. These cycles are described in greater detail in the following sections. Simple Indirect-fired Brayton Cycle Figure 4.R.1 shows a block flow diagram for the simple indirect-fired Brayton cycle. A working fluid, which may be a pure substance or a mixture, circulates between a compressor and an expansion turbine. Thermal Figure 4.R.1 Block Flow Diagram for Simple Brayton Cycle Credit: NETL energy is added to the working fluid just prior to the expansion turbine and a cooler is required to lower the temperature of the working fluid after expansion to the desired inlet temperature to the compressor. In an ideal cycle, with an ideal gas working fluid and no irreversibility in the cycle, the cycle efficiency depends only on the cycle pressure ratio and increases monotonically with the pressure ratio.4 For non-ideal cycles, the cycle efficiency as a function of pressure ratio passes through a maximum at some pressure ratio which depends on the working fluid. Figure 4.R.2 shows the cycle efficiency as a function of pressure ratio for three different working fluids with an arbitrary turbine inlet temperature of 700°C. The dashed lines in the figure correspond to ideal cycles in which the turbomachinery isentropic efficiency (η) is 1 and the solid lines correspond to a non-ideal cycle with turbomachinery isentropic efficiencies of 0.9. For each of these cases, heat and pressure losses were neglected so the cycle efficiencies are optimistic. Note the large decrease in efficiency and the introduction of an efficiency maximum for non-ideal cycles compared to ideal cycles (see also Table 4.R.1). 2 QuadrennialTechnologyReview2015PDF Image | Advancing Clean Electric Power Technologies
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