Gas Turbine Performances Improvement using Steam in the Combustion Chamber under Sahara Conditions

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Gas Turbine Performances Improvement using Steam in the Combustion Chamber under Sahara Conditions ( gas-turbine-performances-improvement-using-steam-the-combust )

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252 Oil & Gas Science and Technology – Rev. IFP, Vol. 63 (2008), No. 2 NOMENCLATURE Subscripts and superscripts 1,2,3,4 Positions of the cycle presented by the various elements of the gas turbine a Air Adm Admission Amb Ambient C Compressor CC Combustion chamber manf Manufacturer f Fuel g Combustion gases inj Parameters of injection Iso Standard conditions P Power plant s Steam water T Turbine Ut Net power output INTRODUCTION The use of gas turbines is increasing for producing electric- ity, operating airplanes and for various industrial applica- tions such as, nuclear power plant (NPP), and the petroleum power plant. In the last three decades, improvements in gas turbines have shown their success in increasing the amount of energy output from power stations [1-3]. The basic gas turbine cycle has low thermal efficiency which decreases in the hard climatic conditions of operation, so it is important to look for improved gas turbine based cycles. The gas tur- bine’s performance is highly dependent on ambient tempera- ture which varies considerably between the day and the night, the summer and the winter. The power that it yields, in particular, decreases considerably as ambient temperature increases. Industrial gas turbines are one of the well estab- lished technologies for power generation. Various additional cycle configurations such as reheating, regeneration, inter- cooling and steam injection have been suggested [2, 3]. All of them offer increased performance and increased output compared to a dry gas turbine cycle. Several types of water or steam injection gas turbine cycle (STIG) have been pro- posed in previous studies and the performance characteris- tics of them investigated [1, 4-14]. The exhaust gas from the turbine is used as an energy source in a heat recovery steam generator (HRSG) where energy is transferred from the exhaust gases to the boiler feed water. The high pressure steam is generated from HRSG. The steam is then injected into the combustor. Injection of steam increases the mass flow rate through the expander and so the power output and the efficiency of the turbine increase. Steam injection also helps in reducing the NOx emissions from the gas turbine [15-19]. The amount of steam generated in the HRSG Cf cp, cv c–p f f’ GN h hof k LCV M m· ni p P PC PT R t T T’2 T’4 s w γ Flow coefficient, (-) Specific heats at constant pressure and volume, (J/(kg.K)) A verage (J/(kg.K)) Fuel to air ratio (without injection of steam water) f = m􏰏 f m􏰏 a , ( % ) Fuel to air ratio (with steam water injection) f ' = m􏰏 ' f m􏰏 a , ( % ) Greek λ Δp ηC ηCC ηG ηmec ηT ηTh ε specific heat at constant pressure, Natural gas, (-) Specific enthalpy, (J/kg) Standard specific enthalpy, (J/kg) Polytropic coefficient of the fluid, (-) Lower calorific value of the fuel, (kJ/kg) Molecular mass, (kg/kmol) Mass rate of flow, (kg/s) Fraction of an element in a gas mixture, (-) Pressure, (bar) Power, (W) Absorbed power by the compressor, (W) Power produced by the turbine, (W) Specific constant of gas, (J/(kg.K)) Temperature in, (°C) Temperature in, (K) Isentropic temperature on the outlet side of the compressor, (K) Isentropic temperature on the outlet side of the turbine, (K) Flow steam to flow air ratio, s = Specific work, (J/kg) Isentropic coefficient, γ = cp cv Excess coefficient of air, (-) Drop of pressure, (bar) Isentropic efficiency of the compressor, (%) Combustion efficiency, (%) Electric generator efficiency, (%) Mechanical efficiency, (%) Isentropic output of turbine, (%) Thermal efficiency of the cycle, (%) p Compressor pressure ratio, ε = 2 p1 , (-) m􏰏 s , (%) m􏰏 a , (-)

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