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Combined-Cycle Analysis Assuming a constant heat capacity for the gas turbine combustion gas, we may compare gas temperatures with adjacent HRSG local water temperatures on the T- s diagram, Figure 9.5, by applying the steady-flow First Law of Thermodynamics to appropriate sections of the HRSG: ms(h12 – h11) = mgCpg(T6 – T7) = msA1 ms(h13 – h12) = mgCpg(T5 – T6) = msA2 ms(h8 – h13) = mgCpg(T4 – T5) = msA3 [Btu/hr | kJ/hr] [Btu/hr | kJ/hr] [Btu/hr | kJ/hr] (9.1) (9.2) (9.3) where ms and mg are the mass flow rates for the steam and gas turbine cycles, respectively, and the Ai (i = 1, 2, 3) are the areas on the T-s diagram representing heat transfer per unit mass of steam. By adding the three equations, we obtain the same equation as would result from application of the steady-flow First Law of Thermodynamics to the entire HRSG: ms(h8 – h11) = mgCpg(T4 – T7) =ms(A1 +A2 +A3) [Btu/hr|kJ/hr] (9.4) Thus the enthalpy rise of the steam in the HRSG is controlled by the ratio of mass flow rates and the hot-gas temperature drop. Expressing gas temperature in the HRSG in terms of steam enthalpy allows us to condense these equations into T= T7 +(ms/mgCpg)(h–h11) [R|K] (9.5) It is evident that the gas temperature is linearly proportional to the water enthalpy on a T-h diagram, as shown in Figure 9.6. The abscissa may be viewed as the cumulative heat transfer per unit mass of water, which is in turn proportional to the exhaust gas heat transfer. The temperature difference T6 – T12, known as the pinchpoint temperature difference, is at a critical location in the heat recovery steam generator, because it occurs at the point of minimum temperature difference between the two fluids. It should exceed some minimum design value (about 30°F) for all operating conditions of the system to make effective use of all of the HRSG heat transfer surface. Smaller temperature differences would substantially increase the heat transfer surface area needed, while significantly larger values would necessitate reducing the boiling temperature and would adversely affect the combined-cycle thermal efficiency. 337PDF Image | Advanced Systems Steam Power Plant
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