Steam cooled gas turbine system

Abstract: A steam cooled gas turbine system in a combined power plant, constituted such that gas turbine blade cooling steam (11) and combustor tail pipe cooling steam (16) are bled from an outlet of a high pressure turbine (7), passed through a fuel heater (18) for heat exchange with fuel, sprayed with water (19) to be cooled to predetermined temperatures, and then supplied to cooling areas, whereby the cooling steam supply temperatures can be maintained at predetermined values during partial load operation as well as rated operating to achieve effective cooling.

Description: BACKGROUND OF THE INVENTION This invention relates to a steam cooling process for a gas turbine system in which a gas turbine blade and a combustor tail pipe are steam cooled. A conventional gas turbine system is described with reference to Fig. 2. As shown in Fig. 2, a conventional steam cooled gas turbine is configured such that bleed steam from an outlet of a high pressure turbine is used as such for blade cooling, and then recovered by an intermediate pressure turbine. A tail pipe of a combustor is cooled with discharge air from a compressor. In Fig. 2, the numeral 01 denotes a gas turbine, 02 an exhaust heat recovery boiler, 7 a high pressure turbine, 8 an intermediate pressure turbine, and 9 a low pressure turbine. In the gas turbine 01, the air is sucked into a compressor 5, and compressed there to a predetermined pressure. Then, fuel adjusted to a predetermined temperature at an inlet of a turbine 4 and air pressurized by the compressor 5 are mixed and burnt in a combustor 6. In the turbine 4, a high temperature, high pressure combustion gas generated by the combustor 6 is expanded to produce output, which generates power in a generator 20. Exhaust gas after completion of work is supplied to the exhaust heat recovery boiler 02 through an exhaust gas duct 10. A turbine stationary blade and a turbine moving blade of the turbine 4 are cooled with steam fed from an outlet of the high pressure turbine 7 through a blade cooling steam supply piping 11. Heated steam after cooling is recovered into an inlet of the intermediate pressure turbine 8 via a blade cooling steam recovery piping 12. In the exhaust heat recovery boiler 02, superheated steam produced by a high pressure drum 3 is guided to the high pressure turbine 7 through a high pressure steam piping 13. Then, it is expanded in the high pressure turbine 7 to generate output. Output steam from the high pressure turbine 7 is branched into a portion which is guided to the turbine stationary blade and moving blade of the gas turbine 01 by the blade cooling steam supply piping 11, and a portion which is guided to a reheater 24 of the exhaust heat recovery boiler 02. Steam produced by an intermediate pressure drum 2 is mixed with outlet steam from the high pressure turbine 7. The resulting mixture is supplied to the reheater 24, where it is heated. The heated mixture is mixed with the blade cooling steam guided by the blade cooling steam recovery piping 12, and is then fed to the inlet of the intermediate pressure turbine 8. In the intermediate pressure turbine 8, steam expands to obtain output. Outlet steam from the intermediate pressure turbine 8 mixes with steam, which has been produced by a low pressure boiler 1, via a low pressure steam piping 15. Then, the mixed steam is supplied to the low pressure turbine 9 to obtain output. Then, steam is condensed by a condenser 21, and pressurized by a pressure pump 22 to a predetermined pressure. Then, the condensate is fed to the exhaust heat recovery boiler 02 through a feed water piping 23. As stated earlier, according to the conventional steam cooled gas turbine, steam bled from the outlet of the high pressure turbine is used as blade cooling steam, while air discharged from the compressor is used as such to cool the tail pipe of the combustor. Thus, temperature control for cooling steam has been difficult. Furthermore, the high temperature part of the gas turbine undergoes creep deformation, unless the metal temperature is made lower than a certain temperature. Thus, the supply temperature of cooling steam must be set to be below a certain limit. Under partial load, in particular, the cooling steam supply temperature tends to become higher than under rated load. Utmost care must be exercised about this respect. Document EP 0 674 099 A1 discloses a method for cooling thermally loaded components of a gas turbine group as part of a combined installation which, in addition, also consists of a waste heat steam generator and a steam cycle. With the method according to EP 0 674 099 A1 a quantity of saturated steam is extracted from a drum of the steam cycle. The components mentioned, namely the combustion chamber and the turbine, are cooled in series by this saturated steam and the steam is subsequently returned to a steam turbine of the steam cycle at an appropriate location. The steam, from the steam turbine, employed for cooling is moderated, if required, with a proportion of water from the waste heat steam generator upstream of the components to be cooled. SUMMARY OF THE INVENTION The present invention has been accomplished in the light of these situations. Its object is to provide a steam cooling process for a system which can maintain the cooling steam supply temperature at a predetermined value under partial load as well as rated load, thereby performing effective cooling. The present invention for attaining this object provides a steam cooling process for a steam cooled gas turbine system in a combined cycle power plant which comprises a combination of a gas turbine plant and a steam turbine plant, and includes an exhaust heat recovery boiler for generating steam turbine driving steam by utilizing exhaust heat from a gas turbine; wherein gas turbine blade cooling steam and combustor tail pipe cooling steam bled from an outlet of a high pressure steam turbine are passed through a fuel heater for heat exchange with fuel; then each cooling steam is sprayed with water to be cooled to a predetermined temperature, and is supplied to a cooling area; and the blade cooling steam that has left the cooling area is recovered into an intermediate area of a reheater, while the tail pipe cooling steam that has left the cooling area is recovered into an inlet of an intermediate pressure turbine. According to this gas turbine system, blade cooling steam and combustor tail pipe cooling steam are bled from the outlet of the high pressure turbine, heat-exchanged with fuel by the fuel heater of the gas turbine, and then sprayed with feed water to be cooled to the predetermined temperature, whereby the metal temperature of the combustor tail pipe and turbine blade can be brought down to a level below the allowable temperature. During this process, gas turbine fuel is heated by the fuel heater as stated previously, so that the fuel flow rate can be decreased to increase the efficiency of the combined plant. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a system diagram of a steam cooled gas turbine system concerned with an embodiment of the present invention; and Fig. 2 is a system diagram of a conventional steam cooled gas turbine system. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will now be described with reference to Fig. 1. The same parts as in the conventional system are assigned the same numerals and symbols, and an overlapping explanation is omitted, with the main focus put on the key points of this embodiment. In the instant embodiment, high pressure bleed steam discharged from an outlet of a high pressure turbine 7 is passed through a fuel heater 18 by way of a blade cooling steam supply piping 11 and a tail pipe cooling steam supply piping 16 so as to exchange heat with fuel in a gas turbine. Then, water is fed from a temperature reducing spray water supply piping 19 to each of the blade cooling steam supply piping 11 and the tail pipe cooling steam supply piping 16. A control device (not shown) adjusts the amount of heating of the gas turbine fuel and the flow rate of the spray water for the temperature reducing spray water supply piping 19. Thus, the supply temperature of cooling steam can be controlled at and adjusted to a predetermined temperature during rated operation and partial load operation of the gas turbine 01. In the conventional steam cooled gas turbine system, as aforementioned, cooling steam for the turbine stationary blade and moving blade of the gas turbine is part of bleed steam from the outlet of the high pressure turbine 7. When the inlet temperature of the gas turbine, the inlet guide vane opening, or the atmospheric temperature changes, therefore, the outlet temperature of the high pressure turbine 7 changes accordingly. Thus, the turbine blade cooling steam temperature also changes, thereby simultaneously changing the metal temperature of the turbine blade. Under partial load, in particular, this cooling steam temperature markedly tends to become high, posing a possibility for creep deformation of the turbine blade. In the instant embodiment, on the other hand, the cooling steam supply temperature can be controlled to a predetermined temperature during the rated operation and partial load operation of the gas turbine. Thus, the reliability of the stationary blade and moving blade of the turbine 4 can be ensured, and an improvement in the combined efficiency by fuel heating can be expected. According to the present invention, as described above, gas turbine blade cooling steam and combustor tail pipe cooling steam are taken from bleed air from the high pressure turbine, heat-exchanged in the gas turbine fuel heater, and then sprayed with water, whereby the supply temperatures of the combustor tail pipe cooling steam and the gas turbine blade cooling steam can be set at predetermined temperatures under any operating conditions. Thus, the metal temperatures of the combustor tail pipe and the turbine blade of the gas turbine can be controlled within the allowable temperature range. Furthermore, fuel is heated by heat exchange with cooling steam, so that the combined efficiency can be raised. While the present invention as defined by the claims has been described with reference to the illustrated embodiment, it is to be understood that the invention is not restricted thereby, but various changes and modifications may be made in the concrete structure of the invention without departing from the spirit and scope of the invention. REFERENCE NUMERALS 01 GAS TURBINE 02 RECOVERY BOILER 1 LOW PRESSURE DRUM 2 INTERMEDIATE PRESSURE DRUM 3 HIGH PRESSURE DRUM 4 TURBINE 5 COMPRESSOR 6 COMBUSTOR TAIL PIPE STEAM COOLING 7 HIGH PRESSURE TURBINE 8 INTERMEDIATE PRESSURE TURBINE 9 LOW PRESSURE TURBINE 10 EXHAUST GAS DUCT 11 BLADE COOLING STEAM SUPPLY PIPE 12 BLADE COOLING STEAM RECOVERY PIPING 13 HIGH PRESSURE STEAM PIPING 14 INTERMEDIATE PRESSURE STEAM PIPING 15 LOW PRESSURE STEAM PIPING 16 TAIL PIPE COOLING STEAM SUPPLY PIPING 17 TAIL PIPE COOLING STEAM RECOVERY PIPING 18 FUEL HEATER 19 TEMPERATURE REDUCING SPRAY WATER SUPPLY PIPING 20 GENERATOR 21 CONDENSER 22 PRESSURE PUMP 23 FEED WATER PIPING 24 REHEATER

Claims: Steam cooling process for a steam cooled gas turbine system in a combined cycle power plant which comprises a combination of a gas turbine plant and a steam turbine plant, and includes an exhaust heat recovery boiler for generating steam turbine driving steam by utilizing exhaust heat from a gas turbine (01); wherein gas turbine blade cooling steam and combustor tail pipe cooling steam bled from an outlet of a high pressure steam turbine (7) are passed through a fuel heater (18) for heat exchange with fuel; then each cooling steam is sprayed with water to be cooled to a predetermined temperature, and is supplied to a cooling area; and the blade cooling steam that has left the cooling area is recovered into an intermediate area of a reheater (24), while the tail pipe cooling steam that has left the cooling area is recovered into an inlet of an intermediate pressure steam turbine (8).

Inventors: AOKI SUNAO, HIROKAWA KAZUHARU, MORI HIDETAKA, SUGISHITA HIDEAKI, UEMATSU KAZUO, AOKI, SUNAO, HIROKAWA, KAZUHARU, MORI, HIDETAKA, SUGISHITA, HIDEAKI, UEMATSU, KAZUO, AOKI, Sunao, Mitsubishi Heavy Ind. Ltd., Hirokawa, Kazuharu, Mitsubishi Heavy Ind. Ltd., Mori, Hidetaka, Mitsubishi Heavy Ind. Ltd., Sugishita, Hideaki, Mitsubishi Heavy Ind. Ltd., Uematsu, Kazuo, Mitsubishi Heavy Ind. Ltd.
Applicants: MITSUBISHI HEAVY IND LTD, MITSUBISHI HEAVY INDUSTRIES, LTD.
Application year: 1998
Main classification: F01K23
IPC codes: F01K23, F02C7, F01D9, F01D5