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additional hardware compared to steam systems, but their total volume (approximately 2 m3) represents a small increment. Turbine architecture selection at this size range strongly favors single-stage radial designs. As a result, the physical size of the turbines is quite compact (0.1-0.2m wheel diameter), and the speeds are high (30-35kRPM). The power turbine thus requires a compound epicyclic gearbox to match to a 2-pole generator. However, the smaller single-stage drive turbine matches speed well to a single-stage pump design, allowing for a compact, low-cost design. For sites located in areas in which sub-freezing temperatures are common, the steam turbine, condenser, water treatment and auxiliary systems are typically housed within a turbine house as shown in Figure 8. Due to the skid-mounted arrangement of the EPS100, and its tolerance to extremely low ambient temperatures without risk of freezing of the working fluid, the power generation equipment occupies a much smaller footprint. The elimination of the building and other infrastructure required for the water treatment systems also represents a significant installation cost advantage for sCO2 systems. SGT800: The second example represents a natural scale-up of the EPS100. The Siemens SGT800 is a small industrial gas turbine, which bridges the application space between larger oil and gas applications and small-scale power generation. With a lower pressure ratio than typical aeroderivative gas turbines, and therefore a higher exhaust temperature, the SGT800 is well suited to combined cycle applications. The same sCO2 and steam cycle configurations are used for this larger-scale application. For the sCO2 system, the turbine and pump characteristic curves were used to estimate the projected isentropic efficiency values. The turbines for this configuration are nearing the point where multi-stage axial turbines are able to approach the isentropic efficiency of single-stage radial turbines. The final selection of turbine architecture will require a more detailed study of performance and cost. Using classical turbine scaling guidelines [28], a single stage radial turbine would operate at a speed of approximately 20000RPM, in the range where a single-stage parallel shaft gearbox could drive a 2-pole generator. A multi-stage axial turbine would permit lower shaft speeds, but may result in slightly lower efficiency. For the present, we assume radial designs at this size. The heat exchanger UA’s were allowed to vary to establish the optimal balance between cost and performance as shown in Figure 7, using the cost scaling rules described above. The power-optimized steam point is shown for comparison. Again, the sCO2 system delivers a lower cost solution at a comparable output, or a higher output at a similar cost to the conventional steam system. 2x2x1 GT-7F.04: The third case study is a utility-scale power plant, using two GE GT- 7F.04 gas turbines, two exhaust heat recovery heat exchangers, and a single sCO2 power cycle (a 2x2x1 configuration) to generate approximately 550MW net electrical power. This arrangement is commonly used in steam-based combined cycle gas turbine power plants. This configuration is a significant scale-up (roughly a factor of 20) in sCO2 power output from the current EPS100 system. The challenges and opportunities involved in this scaling are discussed below. 14PDF Image | SUPERCRITICAL CO2 CYCLES FOR GAS TURBINE COMBINED CYCLE
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