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provides a reliable, low emissions power plant burning natural gas fuel. The performance and cost of the CCGT bottoming cycle have substantial effects on the overall plant economics, as up to 35% of the total output is generated by the bottoming cycle. In addition, the bottoming cycle represents a significant fraction of the total combined cycle plant cost. Supercritical CO2 heat recovery systems offer several advantages over existing steam- based systems. The compact size of sCO2 turbomachinery, the elimination of water treatment systems, and the simplicity of the primary heat recovery heat exchanger enable lower capital and installation costs, while advanced cycle designs achieve cycle performance that can match or exceed the incumbent technology. In addition, the non- condensing nature and smaller physical size of sCO2 turbine will reduce maintenance costs, and the elimination of water treatment systems will reduce operating costs. The low freezing point of CO2 (-55°C) also eliminates the need for freeze-protection in cold climates. Finally, although the baseline for comparison in this study is for a water-cooled configuration, sCO2 cycles can also be used in air-cooled configurations, thus allowing for a completely water-free installation. In the present study, we consider the potential improvement of the CCGT system by replacing the steam bottoming cycle with an advanced system utilizing supercritical carbon dioxide (sCO2) in a closed loop heat recovery cycle. SUPERCRITICAL CO2 CYCLE BACKGROUND Supercritical fluid power cycles, and specifically those using carbon dioxide as the working fluid, have been considered as replacements for the steam Rankine cycle since at least the late 1960’s [4,5]. The primary advantage identified by these early authors was that a supercritical fluid (a fluid at a higher pressure than the critical pressure) does not undergo a constant-temperature boiling process during heating. Rather, a continuous reduction in density occurs as the fluid is heated, eliminating the classical heat exchanger “pinch” problem that necessitates complex double or triple pressure heat exchanger arrangements to achieve high steam turbine inlet temperature and cycle efficiency. Carbon dioxide was identified as an advantageous working fluid for these new supercritical cycles due to several factors. It has a relatively low critical pressure (7.38MPa, compared to 22.1MPa for water), allowing for cycle operation well above the critical pressure and vapor dome at working pressures for which process fluid equipment is readily commercially available. It is a relatively safe working fluid, having low toxicity and corrosivity, no flammability, and is thermally stable. Carbon dioxide is a low-cost, readily available fluid with an existing world-wide commercial distribution network. Finally, due to the high density of the fluid throughout the power cycle, the physical size of CO2 equipment is compact. The first documented consideration for sCO2 cycles as gas turbine bottoming cycles dates from the 1970’s, where the potential for heat recovery in a compact physical device garnered some attention for its use in shipboard applications [6]. However, further developments in sCO2 cycles did not occur until the mid-2000’s, at which point interest was renewed in context of their use in advanced nuclear cycles [7,8], and 2PDF Image | SUPERCRITICAL CO2 CYCLES FOR GAS TURBINE COMBINED CYCLE
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