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Model assumptions and process The cycle model is based on the dual rail cycle (Figure 4). The thermodynamic properties of all fluids are calculated by REFPROP 9.1 [19], using the Span & Wagner equation of state for CO2 [20]. The exhaust properties (temperature, flow rate and composition) are taken from GT-ProTM for standard ISO conditions (15°C (59°F) ambient temperature, 60% relative humidity, sea level). The reference bottoming cycle for comparison is a double-pressure steam Rankine system, using the default GT-ProTM options. The cycle model calculates a heat-and work-balanced condition that maximizes the net output power based upon a given cost target. To establish this design-point model, the solver varies overall heat exchanger sizing, turbine flow functions, internal flow splits, pump inlet and outlet pressures, and coolant flow rate. Off-design conditions can then be modeled by maintaining fixed geometry (turbomachinery flow function and efficiency, heat exchanger UA’s and pressure drop characteristics), and solving for the heat- and work-balanced condition, this time only varying certain flow splits and pump inlet pressure, while respecting specified constraints on maximum pressure, minimum stack exit temperature, etc. The various component-level submodels are described below. Turbine flow function (𝐹𝐹 = 𝑤√𝑇/𝑃), with additional models for mechanical (e.g. gearbox and bearing) losses. For design-point calculations, these parameters are input as constant values. When available, detailed performance maps in which these parameters are functions of normalized operating conditions (such as corrected speed and corrected enthalpy drop) may be used to simulate off-design conditions. The largest currently-operating sCO2 turbine is the EPS100 power turbine, a single- stage radial design, with a wheel diameter of approximately 0.24m (9.5 in), and a design-point efficiency of 85% [1]. The maximum practical size of a radial sCO2 turbine is uncertain. Based on physical diameter and tip speed, much larger radial turbines, albeit at a lower shaft power rating, are in commercial service (e.g., [21]). For the purposes of the present study, we assume that the largest practical radial turbine will be approximately 20MW. Using a mean-line radial turbine design code [22], estimated efficiency at the upper end of the radial turbine size range is expected to be in the 86% range. At larger scales, axial turbomachinery will likely be the selected configuration. In Figure 5, axial turbine efficiency vs shaft output power is shown for a variety of steam turbines. The majority of the values are taken from GT-ProTM performance calculations of steam turbines in combined cycle applications. At utility-scale (~ 900MW), steam turbine efficiency can reach as high as 94% [23]. Turbine performance is modeled by two parameters, isentropic efficiency and turbine 9PDF Image | SUPERCRITICAL CO2 CYCLES FOR GAS TURBINE COMBINED CYCLE
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