JPH06323162A - Steam-cooled gas turbine power plant - Google Patents

Abstract

(57) [Abstract] [Purpose] To provide a steam-cooled gas turbine power plant capable of accurately cooling a high temperature part of a gas turbine with cooling steam and stably operating the plant. In a steam-cooled gas turbine power plant that uses cooling steam as a cooling medium for cooling the gas turbine high temperature section 24, a steam compressor 28 is installed in a cooling steam supply pipe 107 for supplying cooling steam to the gas turbine high temperature section 24.
Was installed, and the steam compressor 25 was installed in the heat recovery cooling steam discharge pipe 110 for sending the heat recovery cooling steam after cooling the gas turbine high temperature section 24 to the steam turbine system.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a steam cooling gas turbine power generation plant using steam for cooling a high temperature part of a gas turbine, and particularly to a steam cooling gas turbine power generation plant suitable for accurately cooling the high temperature part of a gas turbine. Regarding

[0002]

2. Description of the Related Art As regards the performance of a gas turbine which uses steam for cooling a high temperature part of a gas turbine, especially a blade, and the basic structure of the system, ASM Paper 87-J.
PGC-GT-1 (ASME paper 87-JP
GC-GT-1) (hereinafter referred to as "technical document"), "closed-circuit steam cooling of gas turbine (Close)
dCircuit Steam Cooling in
Gas Turbines) ".

[0003]

In a combined plant in which a gas turbine and a steam turbine are combined, there is a possibility that the gas turbine inlet temperature can be raised due to the progress of the materials for the high temperature part of the gas turbine and the cooling technology. Because it can be expected to improve efficiency further,
It is becoming the mainstay of future thermal power plants. The inlet temperature of the gas turbine has reached 1300 ° C even under the present circumstances, and is expected to exceed 1500 ° C in the future. However, in the conventional technology using air as a cooling medium,
As the temperature increases, the proportion of air required for cooling increases,
It cannot be expected that the efficiency will be improved by increasing the temperature. It has long been proposed to use steam, which has better performance than air, as the cooling medium for the high temperature part of the gas turbine, but detailed studies have not been carried out because air cooling was sufficient until now.

By applying the steam cooling gas turbine to the combined plant, the heat recovery cooling steam after cooling is recovered in the steam turbine system to increase the output of the steam turbine, or the heat recovery cooling steam after cooling is used in the gas turbine. Since it is possible to increase the output of the gas turbine by mixing it with the combustion gas, studies on the practical application of a combined plant using a steam cooling gas turbine are about to begin.

[0005] In the above-mentioned technical literature, performance study of closed circuit steam cooling in which steam for cooling is extracted from a steam turbine system, a gas turbine is cooled by the steam, and steam heated to a high temperature is returned to the steam turbine system. Results have been reported.
However, no consideration is given to the temperature and pressure requirements of the steam for cooling the gas turbine, and the matching of the steam conditions between the heat recovery cooling steam and the steam turbine system when returning the heat recovery cooling steam to the steam turbine system.

When a member such as a blade of a high temperature portion of a gas turbine is cooled by using steam, the high temperature combustion gas and the cooling steam are in contact with each other at the boundary. In addition, in the joint between the high temperature members, for example, in the joint between the disk and the blade, a small gap is generally provided in consideration of the deformation when the temperature changes. If the pressure is lower than the pressure of the combustion gas, the high temperature combustion gas enters the gap,
If the member temperature in the gap is raised or the combustion gas is mixed with the cooling steam, the cooling steam supply / recovery system cannot be operated. Further, even if a slight crack is generated in the high temperature member due to some obstacle, the high temperature combustion gas is mixed in the cooling steam system.

Further, when the high temperature part of the gas turbine is cooled to increase the thermal efficiency of the plant and the high temperature heat recovery cooling steam is recovered in the steam turbine system, the temperature and pressure of the recovered cooling steam generally match. There are no points in the steam turbine system.

Assuming that the steam conditions of the current combined plant are 538 ° C., 100 ata / 538 ° C., and 25 ata, and the design point operating pressure of the gas turbine is about 15 ata, the cooling steam is discharged at the outlet 25 of the high-pressure steam turbine.
It is considered that the heat recovery cooling steam may be taken from about a ta, and if the heat recovery cooling steam is to be recovered in the steam turbine system in which the temperature is the same, the pressure of the heat recovery cooling steam must be reduced,
This results in energy loss of pressure. In addition, if an attempt is made to flow into a point where the pressures match, there is a problem that thermal stress is generated in the point of inflow due to the temperature difference of the steam.

An object of the present invention is to provide a steam-cooled gas turbine power generation plant capable of accurately cooling a high temperature part of a gas turbine with cooling steam and stably operating the plant.

Another object of the present invention is to provide a steam cooling gas turbine power plant capable of smoothly recovering the heat recovery cooling steam after cooling the high temperature part of the gas turbine to a high pressure level portion of the steam turbine system. Especially.

[0011]

The above object is achieved by installing a steam compressor for boosting the pressure of steam in a cooling steam piping system.

Further, the above object can be achieved by installing a steam compressor in a cooling steam supply pipe for supplying the cooling steam to the high temperature part of the gas turbine.

Further, the above object can be achieved by installing a steam compressor in the heat recovery cooling steam discharge pipe for recovering the heat recovery cooling steam after cooling the high temperature part of the gas turbine.

Further, the above object is to install a steam compressor in a cooling steam supply pipe for supplying cooling steam to the high temperature part of the gas turbine and to recover heat after cooling the high temperature part of the gas turbine to recover the cooling steam. This is achieved by installing a vapor compressor also in the cooling vapor discharge pipe.

The object is to drive and connect the steam compressor to either a gas turbine device or a steam turbine system, and to connect the steam compressor to the steam turbine as a driving device for the steam compressor. By using the low-pressure steam generated in the plant as the driving force for the turbine, the water supply from the steam turbine system is used between the steam compressor installed in the cooling steam supply pipe and the inlet of the high temperature part of the gas turbine. This is achieved by additionally providing cooling steam temperature adjusting means for adjusting the temperature of the cooling steam.

Further, the purpose is to provide a main-stream steam and a heat recovery cooling steam merging part in the steam turbine system, and connect the outlet of the high temperature part of the gas turbine and the merging part by a heat recovery cooling steam discharge pipe to collect the heat. A steam compressor is installed in the cooling steam discharge pipe, and steam temperature adjusting means for adjusting the temperatures of the mainstream steam and the heat recovery cooling steam toward the merging portion, and the pressure of the heat recovery cooling steam toward the merging portion are adjusted. This is achieved by providing steam pressure adjusting means.

The object is to connect the cooling steam extraction part and the inlet of the high temperature part of the gas turbine by a cooling steam supply pipe, install a steam compressor in the cooling steam supply pipe, and further connect the cooling steam to the gas. By providing steam temperature adjusting means for adjusting the temperature of the cooling steam toward the turbine high temperature portion, steam pressure adjusting means for adjusting the pressure of the cooling steam, and steam flow rate adjusting means for adjusting the flow rate of the cooling steam. ,
Even better achieved.

[0018]

In the present invention, a steam compressor for boosting the pressure of steam is installed in the cooling steam piping system.

By the way, the design point operating pressure of a gas turbine in a combined plant is generally selected so as to maximize the efficiency, and the inlet temperature is 1300 ° C to 1600.
In the case of a gas turbine at ℃, it is about 13 to 18 ata. In order to apply steam cooling to these gas turbines, it is necessary to set the pressure of the cooling steam to about 20ata in order to prevent the combustion gas from mixing into the cooling steam system. As described above, the steam of the steam turbine of the combined plant is used. Conditions are 538 ℃, 100ata / 538 ℃, 25
In the case of ata, the cooling steam is 2 at the outlet of the high pressure steam turbine.
It is considered to start from about 5ata. In this case, the temperature of the heat recovery cooling steam after cooling the high temperature part of the gas turbine is not less than the outlet temperature of the high pressure steam turbine and not more than the inlet temperature of the reheat steam turbine. When this heat recovery cooling steam is compressed by the steam compressor installed in the cooling steam piping system, the pressure of the heat recovery cooling steam rises without losing the energy of the temperature and pressure of the heat recovery cooling steam, and the compression power is Heat recovery Cooling steam is recovered as an increase in sensible heat. As a result, the steam condition (temperature and pressure) at the outlet of the steam compressor can be matched with any steam condition (temperature and pressure) in the steam turbine system.

Further, when the cooling steam is supplied from the steam turbine system, the pressure of the cooling steam may not reach the pressure of the combustion gas of the gas turbine device when the plant is started or partially loaded. In such a case, the steam compressor installed in the cooling steam piping system boosts the cooling steam above the pressure of the combustion gas to prevent the combustion gas from entering the cooling steam piping system and stabilize in the high temperature part of the gas turbine. Cooling steam can be supplied.

Further, in the present invention, a steam compressor is installed in the cooling steam supply pipe for supplying the cooling steam to the high temperature part of the gas turbine. As a result, the supply pressure of the cooling steam that cools the high temperature part of the gas turbine can be constantly increased above the combustion pressure of the gas turbine, so that the high temperature combustion gas enters the gap of the gas turbine or the member of the gap part. It is possible to solve the problem that the temperature is raised or the combustion gas is mixed in the cooling steam to hinder the operation of the cooling steam supply and recovery system.

Further, in the present invention, the steam compressor is installed in the heat recovery cooling steam discharge pipe for recovering the heat recovery cooling steam in the high temperature part of the gas turbine. As a result, when the cooling steam after heat recovery in the high temperature part of the gas turbine is mixed and recovered in the steam turbine system, the heat recovery cooling steam is compressed by the steam compressor, and the heat recovery cooling is performed by raising the temperature and pressure. The steam can be mixed and matched with the steam conditions (temperature and pressure) of the recovery destination, and the driving force required for the steam compressor is converted into an increase in sensible heat of the steam, thus operating the plant with high efficiency. be able to.

Moreover, in the present invention, the vapor compressor is installed in the cooling vapor supply pipe, and the vapor compressor is also installed in the heat recovery cooling vapor discharge pipe.

In the combined plant, the operating pressure of the gas turbine and the steam pressure of the steam turbine fluctuate in the process from start-up to rated operation. Therefore, the pressure of the cooling steam supplied from the steam turbine system corresponds to the combustion gas of the gas turbine. There is a time below pressure. When the high temperature part of the gas turbine is cooled by the cooling steam in this pressure state, the combustion gas may enter the steam turbine system and cause corrosion of the equipment of the steam turbine system. Therefore, in the present invention, since the cooling steam can be constantly boosted to a pressure higher than the pressure of the combustion gas of the gas turbine by the steam compressor installed in the cooling steam supply pipe, the combustion gas enters the steam turbine system. Prevent
Stable cooling steam can be supplied to the high temperature part of the gas turbine. Further, in the present invention, the steam condition of the steam compressor (temperature and temperature) is increased by increasing the pressure of the heat recovery cooling steam after cooling the high temperature part of the gas turbine and raising the temperature by the steam compressor installed in the heat recovery cooling steam discharge pipe. Since the pressure) can be matched with the steam conditions (temperature and pressure) of the heat recovery cooling steam mixed and recovered, the heat recovery cooling steam can be smoothly recovered to the steam turbine system.

Further, in the present invention, since the steam compressor is drivingly connected to the gas turbine device or the steam turbine system, the entire plant including the steam compressor can be compactly integrated, and the steam compressor can be driven. It is also possible to reduce the operating cost of the steam compressor as compared with the case where the electric power generated by the generator of the combined plant is used as the power.

Further, in the present invention, a steam turbine is connected as a drive unit for the steam compressor, and low-pressure steam generated in the plant is used as a driving force for the steam turbine.

For example, the steam generated in the low-pressure drum of the exhaust heat recovery boiler has low temperature and pressure, and has low utility value even if recovered in the low-pressure steam turbine of the steam turbine system.
Therefore, in the present invention, since the low pressure steam generated in the low pressure drum or the like is used as the drive source of the steam compressor,
Compared to the case of using the electric power generated by the generator of the combined plant as the drive source of the steam compressor, the efficiency of the generator can be improved, and the rotation speed can be changed only by changing the flow rate of steam supplied to the steam turbine. Since it can be adjusted, the rotation speed of the vapor compressor can be easily controlled.

Furthermore, in the present invention, the steam temperature adjusting means is provided between the steam compressor installed in the cooling steam supply pipe and the inlet of the high temperature part of the gas turbine. Then, the steam temperature adjusting means adjusts the temperature of the cooling steam by using the supplied water from the steam turbine system, for example, by spraying the supplied water onto the cooling steam. Thereby, the temperature of the cooling steam supplied to the high temperature part of the gas turbine can be easily adjusted to an appropriate value.

Further, in the present invention, the steam turbine system is provided with a confluence portion of the mainstream steam and the heat recovery cooling steam. Further, the outlet of the high temperature part of the gas turbine and the confluence part are connected by a heat recovery cooling steam discharge pipe, and a steam compressor is installed in the heat recovery cooling steam discharge pipe. Furthermore, steam temperature adjusting means for adjusting the temperatures of the mainstream steam and the heat recovery cooling steam toward the merging portion, and steam pressure adjusting means for adjusting the pressure of the heat recovery cooling steam toward the merging portion are provided.

When the heat recovery cooling steam after cooling the high temperature part of the gas turbine is recovered in the steam turbine system, the steam conditions (temperature and pressure) of the mainstream steam of the steam turbine system with respect to the steam conditions of the heat recovery cooling steam ( Temperature and pressure) must be adapted. Regarding the pressure relationship, make sure that the mainstream steam of the steam turbine system does not flow back into the heat recovery cooling steam pipe.
The pressure P ₁ of the heat recovery cooling steam must be at least higher than the pressure P _{2 of the} mainstream steam. However, the pressure P ₁
Is larger than the pressure P ₂ , the pressure loss of the heat recovery cooling steam becomes large and the output is lowered. Therefore, when the allowable pressure difference is A, A> P ₁ -P ₂ > 0. Regarding the temperature relationship, if the temperature difference between the temperature T ₁ of the heat recovery cooling steam and the temperature T _{2 of the} mainstream steam is too large,
Thermal stress is generated in the confluence, which may damage the equipment.
Therefore, when the allowable temperature difference is B, B> | T ₁ −T ₂ |
Try to be.

Therefore, in the present invention, the heat recovery cooling steam is compressed by the steam compressor installed in the heat recovery cooling steam discharge pipe, and the temperature of the heat recovery cooling steam is increased and sent to the merging portion. At that time, the pressure P ₁ of the heat recovery cooling steam to fit the aforementioned _{A> P 1 -P 2> 0} , adjusted by the steam pressure adjusting means with respect to the pressure P ₂ of the main steam toward the merging portion. At the same time, and the temperature T ₁ of the temperature T ₂ and the heat recovery cooling steam mainstream steam described above B> | T
Adjust by steam temperature adjusting means so that it falls within _1- T ₂ |. As a result, the mainstream steam and the heat recovery cooling steam can be combined into the merging portion at appropriate values in terms of pressure and temperature, and the heat recovery cooling steam can be recovered in the steam turbine system in an appropriate state.

In the present invention, the cooling steam extraction pipe from the plant and the inlet of the gas turbine high temperature part are connected by a cooling steam supply pipe, and a steam compressor is installed in the cooling steam supply pipe. Furthermore, steam temperature adjusting means for adjusting the temperature of the cooling steam from the steam compressor toward the high temperature part of the gas turbine, and steam pressure adjusting means for adjusting the pressure of the cooling steam,
A steam flow rate adjusting means for adjusting the flow rate of the cooling steam is provided.

When the cooling steam is supplied to the high temperature part of the gas turbine, the pressure P _{3 of the} cooling steam is set so that the combustion gas of the gas turbine device does not enter the cooling steam supply pipe from the high temperature part of the gas turbine. Must be greater than P ₄ . However, if the pressure difference between the pressure P ₃ and the pressure P ₄ is too large, the cooling steam supply pipe may be broken,
Further, in the case of closed-circuit steam cooling, there is an upper limit value of the pressure difference because the amount of cooling steam leaking to the combustion gas increases. Therefore,
When the allowable pressure difference is C, C> P ₃ −P ₄ > 0. Further, the temperature T _{3 of the} high temperature part of the gas turbine is
Due to problems with the material of the high temperature part of the gas turbine, its allowable temperature T
Must not exceed. Therefore, TT
₃ > 0 must be set.

Therefore, in the present invention, the cooling steam is compressed by the steam compressor installed in the cooling steam supply pipe, and the pressure is increased and sent to the high temperature part of the gas turbine. Along the way, the steam pressure adjusting means the pressure P ₃ of the cooling steam adjusting to fit the C> P ₃ -P _4> 0 with respect to the pressure P ₄ of the combustion gases. Further, the steam temperature adjusting means adjusts T ₃ of the cooling steam so that T−T ₃ > 0 in relation to the above-mentioned allowable temperature T. Further, the flow rate of the cooling steam is adjusted by the steam flow rate adjusting means so as to be appropriate.

As a result, the temperature, the pressure and the flow rate of the cooling steam can be adjusted to appropriate values with respect to the temperature of the high temperature part of the gas turbine and the pressure of the combustion gas and supplied to the high temperature part of the gas turbine.

[0036]

Embodiments of the present invention will be described below with reference to the drawings.

(First Embodiment) FIG. 1 is a system diagram showing a first embodiment of the present invention.

In the first embodiment shown in this figure, a gas turbine device, an exhaust heat recovery boiler 5, a steam turbine system,
A steam compressor 25 installed in the cooling steam piping system of the gas turbine high temperature section 24 is provided. Further, in this embodiment, the gas turbine device, the generator 4 and the steam turbine system are connected on the same shaft to constitute a single-shaft combined power generation plant.

The gas turbine device is an air compressor 1.
And a combustor 2 and a gas turbine 3. The air compressor 1 is provided with a gas turbine air intake 111, and the combustor 2 is provided with a fuel supply pipe 11
2 is connected.

The exhaust heat recovery boiler 5 is connected to a combustion gas outlet of the gas turbine 3 via a combustion gas supply pipe line 200. The exhaust heat recovery boiler 5 includes a low pressure economizer 9, a low pressure drum 6, a low pressure evaporator 10, a medium pressure economizer 11, a medium pressure drum 7, and a medium pressure evaporator 12.
A high pressure economizer 13, a high pressure drum 8, a high pressure evaporator 14, a superheater 15, a reheater 16, an intermediate pressure pressurizing pump 17, and a high pressure pressurizing pump 18.

The steam turbine system includes a high pressure steam turbine 19, a reheat steam turbine 20, and a low pressure steam turbine 2.
1, a condenser 22, and a water supply pump 23.

The water supply pipe 108 from the condenser 22 is connected to the low pressure economizer 9 in the exhaust heat recovery boiler 5 via the water supply pump 23. The outlet of the low-pressure economizer 9 is connected to the low-pressure drum 6 and at the same time connected to the medium-pressure pressurizing pump 17 and the high-pressure pressurizing pump 18. The outlet pipe of the intermediate pressure pressurizing pump 17 is connected to the intermediate pressure drum 7 via the intermediate pressure economizer 11.
The pipe at the outlet of the high-pressure pressurizing pump 18 is connected to the high-pressure drum 8 via the high-pressure economizer 13.

A main steam pipe 100 is connected to an outlet of the superheater 15 in the exhaust heat recovery boiler 5, and the main steam pipe 100 is connected to a high pressure steam turbine 19 of a steam turbine system. A reheated steam return pipe 101 is connected to an outlet of the high-pressure steam turbine 19, and the reheated steam return pipe 101 is connected to a reheater 16 in the exhaust heat recovery boiler 5. In the middle of the reheated steam return pipe 101, the pipe 10 from the intermediate pressure drum 7 in the exhaust heat recovery boiler 5 is also provided.
2 is connected. A reheat steam pipe 103 is connected to an outlet of the reheater 16, and the reheat steam pipe 103 is connected to a reheat steam turbine 20 of a steam turbine system.
A pipe 105 is connected to the outlet of the low pressure drum 6 in the exhaust heat recovery boiler 5, and the pipe 105 is connected to the low pressure steam turbine 21 of the steam turbine system through a pipe 104 connected to the pipe 105. An outlet pipe of the reheat steam turbine 20 is connected in the middle of 105. The outlet of the low-pressure steam turbine 21 and the condenser 22 are connected by a pipe line 106.

By the way, inside the gas turbine 3, there is a gas turbine high temperature section 24 which needs to be cooled at a high temperature.
The high temperature part 24 of the gas turbine includes a high pressure steam turbine 1
The cooling steam supply pipe 107 is connected from the outlet of 9,
A water spray pipe 109 is connected to the cooling steam supply pipe 107 from a water supply pipe 108 via a pressurizing pump 27. The water spray pipe 109 and the pressurizing pump 27 form a steam temperature adjusting means for adjusting the temperature of the cooling steam. A cooling steam discharge pipe 110 is connected to the outlet of the gas turbine high temperature section 24.
10 is connected to the middle of the reheater 16 in the exhaust heat recovery boiler 5 via the vapor compressor 25 to form a closed circuit.

A compressor driving device 26 is connected to the vapor compressor 25.

Next, the operation of the first embodiment will be described.

Air is taken into the air compressor 1 of the gas turbine apparatus through the gas turbine air intake port 111, the pressure of the air is increased in the air compressor 1, and high-pressure and high-temperature air is supplied to the combustor 2. . Fuel is supplied to the combustor 2 through the fuel supply pipe 112, and the high-pressure and high-temperature air burns the fuel in the combustor 2 to generate high-temperature combustion gas. This high-temperature combustion gas is supplied to the gas turbine 3 and expanded to generate power. Then, the gas turbine 3 drives the air compressor 1 and the generator 4.

The combustion gas discharged from the gas turbine 3 is supplied to the exhaust heat recovery boiler 5 through the combustion gas supply pipe line 200. On the other hand, in the exhaust heat recovery boiler 5, the water supply sent from the condenser 22 is boosted by the water supply pump 23, and the water supply pipe 1
It is supplied to the low pressure economizer 9 through 08. In this low-pressure economizer 9, the feed water at the outlet is sent to the low-pressure drum 6 while being pressurized by the medium-pressure pressurizing pump 17 and recirculated to the low-pressure economizer 9 or sent to the medium-pressure drum 7 through the medium-pressure economizer 11. In addition, low pressure economizer 9
The water supply at the outlet of is pressurized by the high-pressure pressurizing pump 18,
It is sent to the high-pressure drum 8 through the high-pressure economizer 13. Then, the feed water sent to the high-pressure drum 8 is evaporated by the high-pressure evaporator 14 connected to the high-pressure drum 8, the steam thereof is superheated, and is supplied to the high-pressure steam turbine 19 of the steam turbine system through the main steam pipe 100. High pressure steam turbine 1
Power is generated at 9 to drive the generator 4. The steam that has worked in the high-pressure steam turbine 19 is supplied to the reheater 16 through the reheated steam return pipe 101. At the inlet of the reheater 16, the medium pressure evaporator 1 connected to the medium pressure drum 7
Mix the vapors vaporized in 2. The steam reheated by the reheater 16 is supplied to the reheat steam turbine 20 through the reheat steam pipe 103, generates power in the reheat steam turbine 20, and drives the generator 4. The steam that has generated power in the reheat steam turbine 20 is supplied to the low-pressure steam turbine 21 through the pipe 104. The low-pressure steam turbine 21 is also supplied with the steam evaporated in the low-pressure evaporator 10 connected to the low-pressure drum 6 through the pipes 105 and 104. In the low-pressure steam turbine 21, power is generated by these steams and the generator 4 To drive. The steam generated by the low-pressure steam turbine 21 is sent to the condenser 22 through the pipe 106 and condensed in the condenser 22.

The high temperature part 24 of the gas turbine 3 is cooled by the high temperature part 24 of the high pressure steam turbine 19 from the outlet of the high pressure steam turbine 19 through the cooling steam supply pipe 107. Used as steam. In the cooling steam supply pipe 107, the pressure of the water supplied from the water supply pipe 108 is increased by the pressurizing pump 27,
By spraying the cooling steam with water through the water spray pipe 109, the temperature of the cooling steam is reduced. By reducing the temperature of the cooling steam, it is possible to suppress an increase in the temperature of the gas turbine high temperature portion 24 and reduce the burden on the material of the gas turbine high temperature portion 24. The cooling steam passes through the high temperature part of the gas turbine 24, recovers heat from this part, is heated, and loses a pressure of several ata. Assuming that the heat recovery cooling steam after cooling the high temperature part of the gas turbine 24 is directly injected into the steam turbine system, there is no place in the steam turbine system where the temperature and the pressure match, and the thermal stress of the steam mixing part is considered. Then, the pressure must be reduced considerably.

Therefore, in the first embodiment, the heat recovery cooling steam after cooling the gas turbine high temperature section 24 is supplied to the steam compressor 2
5, the vapor compressor 25 rotatably driven by the compressor drive device 26 raises the temperature and raises the pressure, so that it can be injected in the middle of the reheater 16 where the temperature and the pressure match.

Thus, according to this first embodiment,
Required for the steam compressor 25 by making the steam conditions (temperature and pressure) of the heat recovery cooling steam after cooling the gas turbine high temperature part 24 match the steam conditions (temperature and pressure) when mixed and recovered in the steam turbine system. Since a large driving force is converted into sensible heat of steam, a highly efficient steam cooling system can be obtained.

(Second Embodiment) FIG. 2 is a system diagram showing a second embodiment of the present invention.

In the second embodiment shown in this figure, the steam compressor 28 is provided in the middle of the cooling steam supply pipe 107 connecting the outlet of the high-pressure steam turbine 19 and the inlet of the gas turbine high temperature section 24.
Is installed. A compressor drive device 29 is connected to the vapor compressor 28.

Further, a water spray pipe 109 is connected from a water supply pipe 108 via a pressurizing pump 27 to a pipe line between the outlet of the vapor compressor 28 and the inlet of the gas turbine high temperature section 24 in the cooling steam supply pipe 107. ing.

Then, the cooling steam extracted from the outlet of the high-pressure steam turbine 19 is boosted in pressure by using the steam compressor 28, and then cooled by spraying water on the cooling steam by the water spray pipe 109 and the pressurizing pump 27. The gas is supplied to the high temperature part 24 of the gas turbine through the cooling steam supply pipe 107.

In a combined plant in which a gas turbine and a steam turbine are combined, the operating pressure of the gas turbine device and the steam pressure of the steam turbine system fluctuate during the process from startup to rated operation. It exists while the pressure of the steam is lower than the pressure of the combustion gas of the gas turbine system. If the gas turbine high temperature part 24 is cooled in this pressure state, the combustion gas will enter the steam turbine system and cause corrosion of the steam turbine system equipment.

Therefore, in the second embodiment, the cooling steam extracted from the outlet of the high pressure steam turbine 19 is supplied to the steam compressor 2
Since the pressure of the combustion gas is raised to a value higher than that of the combustion gas by using No. 8 and is supplied to the high temperature portion 24 of the gas turbine, it is possible to prevent pressure reversal between the cooling steam and the combustion gas. Therefore, it becomes possible to eliminate the corrosion of the steam turbine system equipment due to the combustion gas entering the steam turbine system.

The other structure and operation of the second embodiment are similar to those of the first embodiment.

(Third Embodiment) FIG. 3 is a system diagram showing a third embodiment of the present invention.

In the third embodiment shown in this figure, the outlet side of the low pressure drum 6 of the exhaust heat recovery boiler 5 is connected to the inlet of the gas turbine high temperature section 24 via the cooling steam supply pipe 201. The cooling steam supply pipe 201 is connected to the steam compressor 2
8 is connected.

The steam generated from the low-pressure drum 6 of the exhaust heat recovery boiler 5 has low temperature and pressure, and even if recovered in the low-pressure steam turbine 21, it has low utility value.

Therefore, in the third embodiment, the steam from the low-pressure drum 6 is guided to the steam compressor 28 through the cooling steam supply pipe 201, and the steam compressor 28 boosts the pressure to cool the high temperature part 24 of the gas turbine. The steam turbine system can be used as steam and can be recovered at a higher pressure level, so that the output of the steam turbine system can be increased.

The other structure and operation of the third embodiment are the same as those of the second embodiment.

(Fourth Embodiment) FIG. 4 is a system diagram showing a fourth embodiment of the present invention.

In the fourth embodiment shown in this figure, the outlet side of the low-pressure drum 6 of the exhaust heat recovery boiler 5 is connected to the inlet of the gas turbine high temperature section 24 via the cooling steam supply pipe 201, and the cooling steam supply The vapor compressor 28 is installed in the pipe 201. On the other hand, the outlet of the steam compressor 25 is connected to the inlet of the high-pressure steam turbine 19 of the steam turbine system via a heat recovery cooling steam return pipe 202.

Then, the steam generated in the low-pressure drum 6 is sent to the steam compressor 28 via the cooling steam supply pipe 201, the pressure is raised by the steam compressor 28, and this is sent to the gas turbine high temperature section 24 as cooling steam. Further, the heat recovery cooling steam after cooling the high temperature part of the gas turbine 24 is sent to the steam compressor 25 via the heat recovery cooling steam discharge pipe 110, the steam compressor 25 raises the temperature and pressure, and the heat recovery cooling return pipe. It is sent to the high-pressure steam turbine 19 through 202.

As described above, the low-utility steam generated from the low-pressure drum 6 of the exhaust heat recovery boiler 5 is used as the cooling steam, and the heat recovery cooling steam after cooling the gas turbine high temperature section 24 is used as the steam compressor 25. To raise and raise the pressure,
Since it is collected at a place with a high pressure level,
Also in the fourth embodiment, the output of the steam turbine system can be increased.

The other structure and operation of the fourth embodiment are the same as those of the third embodiment.

(Fifth Embodiment) FIG. 5 is a system diagram showing a fifth embodiment of the present invention.

In the fifth embodiment shown in this figure, in the gas turbine high temperature section 24, the reheated steam return pipe 101 between the high pressure steam turbine 19 of the steam turbine system and the reheater 16 of the exhaust heat recovery boiler 5 is provided. The cooling steam supply pipe 107 is connected. A vapor compressor 28 is installed in the cooling vapor supply pipe 107, and a compressor drive device 29 is connected to the vapor compressor 28. Cooling steam supply pipe 10 between the outlet of the steam compressor 28 and the inlet of the gas turbine high temperature section 24.
A water spray pipe 1 having a pressure pump 27 at the portion 7
09 is connected. And the gas turbine high temperature part 2
The heat recovery cooling steam after cooling 4 is configured to be usable as a working medium of the gas turbine 3.

As a result, in the fifth embodiment, the cooling steam exiting the high-pressure steam turbine 19 of the steam turbine system is boosted by the steam compressor 28, and the feed water boosted by the pressurizing pump 27 is sprayed with water. Water is sprayed through the pipe 109 to adjust the temperature, and then supplied to the high temperature part 24 of the gas turbine to cool this part. The heat recovery cooling steam after cooling the gas turbine high temperature section 24 is the gas turbine 3
Used as a working medium of.

Therefore, according to the fifth embodiment, the steam after cooling the high temperature part 24 of the gas turbine is used as the working medium of the gas turbine 3,
The output of the gas turbine 3 can be increased, so that the equipment of the steam turbine system can be reduced. Moreover, since the pressure for extracting the cooling steam from the high-pressure steam turbine 19 can be made lower, the steam turbine system can be maintained at high efficiency.

The other structure and operation of the fifth embodiment are similar to those of the second embodiment.

(Sixth Embodiment) FIG. 6 is a system diagram showing a sixth embodiment of the present invention.

In the sixth embodiment shown in this figure, the outlet of the gas turbine high temperature section 24 and the reheater 16 of the exhaust heat recovery boiler 5 are used.
And are connected by a heat recovery cooling steam discharge pipe 110. A steam compressor 25 is installed in the middle of the heat recovery cooling steam discharge pipe 110. A steam turbine 32 is connected to the steam compressor 25 as a compressor drive device. The steam turbine 32 has an exhaust heat recovery boiler 5
The steam supply pipe 203 is connected from the low pressure drum 6 side of the steam turbine 32, and the steam return pipe 204 is connected from the steam turbine 32 to the pipe line 106 between the low pressure steam turbine 21 and the condenser 22 of the steam turbine system. .

Therefore, in the sixth embodiment, the steam generated in the low-pressure drum 6 drives the steam turbine 32 which is a compressor driving device of the steam compressor 25, and the steam turbine 32 rotates the steam compressor 25. When driven, the temperature of the heat recovery cooling steam is raised and increased, and the steam is sent to the reheater 16. On the other hand, the steam after driving the steam turbine 32 is the pipeline 106 between the low-pressure steam turbine 21 and the condenser 22.
Sent to.

When the steam compressor 25 is driven by an electric motor, the electric power used as a drive source of the electric motor is generally gas turbine 3 or high pressure, medium pressure, low pressure steam turbine 1
The electric power generated by driving the generator 4 with the power of 9, 20, 21 is used. Therefore, the substantial efficiency of the generator 4 is reduced.

On the other hand, according to the sixth embodiment, since the steam compressor 25 is driven by the steam turbine 32 which does not need to take the substantial efficiency of the generator 4 into consideration, power generation is performed. You can increase the output of machine 4,
Since the rotation speed of the steam compressor 25 can be adjusted simply by changing the amount of steam supplied to the steam turbine 32, the rotation speed of the steam compressor 25 can be easily controlled.

The other structure and operation of the sixth embodiment are the same as those of the first embodiment.

(Seventh Embodiment) FIG. 7 is a system diagram showing a seventh embodiment of the present invention.

In the seventh embodiment shown in this figure, a steam compressor 34 is drivingly connected to the steam turbine system. The steam compressor 34 and the outlet of the gas turbine high temperature section 24 are connected by a heat recovery cooling steam discharge pipe 205, and the steam compressor 34 and the reheater 16 of the exhaust heat recovery boiler 5 are heat recovery cooling steam. It is connected by a return pipe 206.

In the seventh embodiment, the heat recovery cooling steam after cooling the gas turbine high temperature section 24 is introduced into the steam compressor 34 through the heat recovery cooling steam discharge pipe 205, and the steam compressor 34 is used. After the temperature is raised and the pressure is increased, it is sent to the reheater 16 through the heat recovery cooling steam return pipe 206.

As described above, according to the seventh embodiment, since the steam compressor 34 for compressing the heat recovery cooling steam after cooling the high temperature part 24 of the gas turbine is drivingly connected to the steam turbine system, The entire plant can be compactly integrated.

The vapor compressor 34 may be drivingly connected to the gas turbine device side.

The other structure and operation of the seventh embodiment are the same as those of the first embodiment.

(Eighth Embodiment) Next, FIG. 8 is a system diagram showing an eighth embodiment of the present invention.

In the eighth embodiment shown in this figure, the inlet of the gas turbine high temperature section 41 is connected to the steam turbine system 40 via a cooling steam supply pipe 42. Further, the steam turbine system 40 is provided with a confluent part 43 of the mainstream steam and the heat recovery cooling steam emitted from the high temperature part 41 of the gas turbine, and a water supply system 47 to an exhaust heat recovery boiler (not shown). ing.

The outlet of the gas turbine high temperature section 41 and the merging section 43 are connected by a heat recovery cooling steam discharge pipe 44. A vapor compressor 45 is installed in the middle of the heat recovery cooling vapor discharge pipe 44. A compressor drive device 46 is connected to the vapor compressor 45.

First and second water spray pipes 48 and 49 are connected to the water supply system 47.

The first water spray pipe 48 is provided with a first pressurizing pump 50 and a first valve 52, and the first water spray pipe 48 is compressed by the vapor compressor 45. After the temperature is raised and the pressure is increased, water is sprayed onto the heat recovery cooling steam that flows toward the confluence section 43. The second water spray pipe 49 is provided with a second pressurizing pump 51 and a second valve 53, and the second water spray pipe 49 is provided for the mainstream steam flowing toward the merging portion 43. It is designed to be sprayed with water.

In the heat recovery cooling steam discharge pipe 44, there is provided a first temperature measuring device 54 for measuring the temperature T ₁ of the heat recovery cooling steam which is heated and pressurized by the steam compressor 45 and is directed to the confluence section 43. First pressure measuring device 56 for measuring the pressure P ₁
And are provided. On the other hand, the steam turbine system 40 is provided with a second temperature measuring device 55 for measuring the temperature T _{2 of the} mainstream steam toward the merging portion 43 and a second pressure measuring device 57 for measuring the pressure P _2. ing.

The first and second water spray pipes 48, 49
The first and second valves 52 and 53 provided in the are connected to a valve opening / closing control device 58, and the valve opening / closing control device 58 is connected to the first and second temperature measuring devices 54 and 55. There is. Further, a compressor rotation speed control device 59 is connected to the compressor drive device 46 of the vapor compressor 45, and the compressor rotation speed control device 59 is connected to the first and second compressor rotation speed control devices 59.
The second pressure measuring devices 56 and 57 are connected.

In the eighth embodiment constructed as described above,
Cooling steam for cooling the high temperature part of the gas turbine is extracted from the steam turbine system 40, and this cooling steam is supplied to the high temperature part 41 of the gas turbine through the cooling steam supply pipe 42 to cool this part.

The heat recovery cooling steam after cooling the high temperature part 41 of the gas turbine is sent to the steam compressor 45 through the heat recovery cooling steam discharge pipe 44, and is compressed by the steam compressor 45 to be heated and pressurized. , Heat recovery cooling steam exhaust pipe 4
It is sent to the confluence part 43 through 4. In the meantime, the temperature T ₁ and the pressure P ₁ of the heat recovery cooling steam flowing out of the vapor compressor 45 toward the confluence section 43 are measured by the first temperature measuring device 54 and the first pressure measuring device 56, respectively, and The temperature T ₁ measured by the temperature measuring device 54 is sent to the valve opening / closing control device 58, and the pressure P ₁ measured by the first pressure measuring device 56 is sent to the compressor rotation speed control device 59.

On the other hand, from the steam turbine system 40 to the confluence section 43.
Towards temperature T ₂ and pressure P ₂ of the main steam flow is measured by the second temperature measuring device 55 and the second pressure measuring device 57, respectively, temperature T ₂ measured by the second temperature measuring device 55 The pressure P sent to the valve opening / closing control device 58 and measured by the second pressure measuring device 57
₂ is sent to the compressor rotation speed control device 59.

A first water spray pipe 48 having the first pressurizing pump 50 and the first valve 52, and a second water spray pipe 49 having the second pressurizing pump 51 and the second valve 53. And the valve opening / closing control device 58 constitute a steam temperature adjusting means of the heat recovery cooling steam. The compressor rotation speed control device 59 constitutes a steam pressure adjusting means for controlling the rotation speed of the steam compressor 45 via the compressor drive device 46 and adjusting the pressure of the heat recovery cooling steam.

By the way, regarding the relationship between the pressures P ₁ and P ₂ ,
At least the pressure P _{1 is set} to the pressure P ₂ so that the mainstream steam of the steam turbine system 40 does not flow back to the heat recovery cooling steam discharge pipe 44.
Must be greater than. However, if the pressure P ₁ is too large compared to the pressure P ₂ , the pressure loss of the heat recovery cooling steam becomes large and the output is lowered. Therefore, regarding pressures P ₁ and P ₂ , when A is the allowable pressure difference, the relational expression shown by the following equation 1 is established.

[0098] The number _{1 A> P 1 -P 2>} 0 In addition, the relationship between the temperature T _1, T _2, the temperature T ₁ and the temperature T ₂
If the temperature difference is too large, thermal stress is generated in the confluence portion 43, which may damage the equipment. Therefore, regarding the temperatures T ₁ and T ₂ , when B is the allowable temperature difference, the relational expression shown by the following equation 2 is established.

Equation 2 B> | T ₁ −T ₂ | As can be seen from the above, it is necessary to keep the temperature T ₁ and the pressure P ₁ of the heat recovery cooling steam at appropriate values.

Therefore, the compressor rotation speed control device 59 takes in the pressure P ₁ of the heat recovery cooling steam from the first pressure measuring device 56 and takes in the pressure P _{2 of the} mainstream steam from the second pressure measuring device 57 to obtain P ₁ −P ₂ is calculated, and when the pressure difference becomes equal to or larger than the allowable pressure difference A in the pressure relational expression, the rotation of the steam compressor 45 is instructed by the command from the compressor rotation speed control device 59 to the compressor drive device 46. The pressure P ₁ is reduced so that the allowable pressure difference A can be accommodated. On the contrary, the pressure difference is 0
When approaching, the rotation speed of the vapor compressor 45 is increased by a command from the compressor rotation speed control device 59 to the compressor drive device 46, and the pressure P ₁ is increased so that the allowable pressure difference A is reached. By the above control, the pressure P ₁ of the heat recovery cooling steam can be maintained at an appropriate value.

On the other hand, the valve opening / closing control device 58 takes in the temperature T ₁ of the heat recovery cooling steam from the first temperature measuring device 54 and takes the temperature T _{2 of the} mainstream steam from the second temperature measuring device 55.
Is taken in, T ₁ −T ₂ is calculated, and B <
In the case of T ₁ -T ₂ , the temperature T ₁ of the heat recovery cooling steam is too high with respect to the temperature T ₂ of the mainstream steam of the steam turbine system 40, so the first command is issued from the valve opening / closing control device 58.
Open the valve 52, exit the vapor compressor 45, and join the confluence section 43.
The water taken in from the water supply system 47 is pressurized by the first pressurizing pump 50 to the heat recovery cooling steam toward and the allowable temperature difference B is obtained by spraying the water with the first water spray pipe 48.
Reduce the temperature so that In the temperature relational expression, B <
When the temperature becomes T ₂ −T ₁ , the temperature T ₂ of the mainstream steam of the steam turbine system 40 is too high with respect to the temperature T ₁ of the heat recovery cooling steam. The valve 53 is opened, and water taken from the water supply system 47 is added to the second pressurizing pump 5 as mainstream steam flowing toward the merging portion 43.
The pressure is raised at 1 and water is sprayed through the second water spray pipe 49 to reduce the temperature so that the allowable temperature difference B is reached.

By the above control, the temperature difference between the mainstream steam and the heat recovery cooling steam can be maintained at an appropriate value.

Therefore, according to this eighth embodiment,
When the heat recovery cooling steam after cooling the gas turbine high temperature part 41 is joined to the steam turbine system 40, the temperature and pressure of the main recovery steam of the steam turbine system 40 are set to the temperature and pressure of the heat recovery cooling steam at the joining part 43. Can be adapted,
It is possible to operate the plant in a stable state.

(Ninth Embodiment) FIG. 9 is a system diagram showing a ninth embodiment of the present invention.

The ninth embodiment shown in this figure is applied to a plant of the type in which the heat recovery cooling steam after cooling the gas turbine high temperature section 24 is used as the working medium of the gas turbine 3. Further, in the ninth embodiment, the inlet of the gas turbine high temperature section 24 is connected to the steam turbine system 60 via the cooling steam supply pipe 61.

A vapor compressor 62 is installed in the middle of the cooling vapor supply pipe 61, and a compressor drive device 63 is connected to the vapor compressor 62. Further, a cooling steam bypass 64 is provided from a portion of the cooling steam supply pipe 61 between the steam compressor 62 and the gas turbine high temperature portion 24 to a portion between the steam turbine system 60 and the steam compressor 62. A bypass valve 65 is provided in the.

A third pressure measuring device 66 for measuring the pressure P _{3 of the} cooling steam is provided near the high temperature part 24 of the gas turbine in the cooling steam supply pipe 61. Also,
A fourth pressure measuring device 67 for measuring the pressure P _{4 of the} combustion gas is provided in the pipe extending from the air compressor 1 to the combustor 2 of the gas turbine device. Furthermore, the gas turbine 3
To measure the temperature T ₃ of the high temperature part of the gas turbine 24
The temperature measuring device 68 is provided. An allowable temperature setter 69 for setting the allowable temperature T is connected to the third temperature measuring device 68.

A water spray pipe 70 is connected between the steam turbine system 60 and a portion of the cooling steam supply pipe 61 near the high temperature part 24 of the gas turbine. The water spray pipe 70 is provided with a pressure pump 71 and a valve 72.

The third and fourth pressure measuring devices 66, 67
Is connected to the compressor rotation speed control device 73. This compressor rotation speed control device 73 includes the compressor drive device 6
3 is connected. On the other hand, the third temperature measuring device 6
Reference numeral 8 is connected to the valve opening / closing control device 74. The bypass valve 65 and the valve 72 provided in the water spray pipe 70 are connected to the valve opening / closing control device 74.

Bypass 64 having the bypass valve 65
The valve opening / closing control device 74 constitutes a steam flow rate adjusting means for adjusting the flow rate of the cooling steam. Further, a water spray pipe 70 having the pressurizing pump 71 and the valve 72.
The valve opening / closing control device 74 constitutes steam temperature adjusting means for adjusting the temperature of the cooling steam. The compressor rotation speed control device 73 constitutes a steam pressure adjusting means for controlling the rotation speed of the steam compressor 62 via the compressor driving device 63 and adjusting the pressure of the cooling steam.

In the ninth embodiment, the pressure P ₃ of the cooling steam at the inlet of the gas turbine high temperature section 24 is measured by the third pressure measuring device 66, and the pressure P ₃ is used as the compressor rotation speed. It is sent to the control device 73. Further, the pressure P ₄ of the combustion gas of the air compressor 1 of the gas turbine device is measured by the fourth pressure measuring device 67, and the pressure P ₄ is also sent to the compressor rotation speed control device 73.

Here, regarding the relationship between the pressure P ₃ and the pressure P ₄ , in order to prevent the combustion gas from entering the cooling steam supply pipe 61 of the high temperature section 24 of the gas turbine, the pressure P _{3 of the} cooling steam is set. It must be higher than the combustion gas pressure P ₄ . However, if the pressure difference between the pressure P ₃ and the pressure P ₄ is too large, the cooling steam supply pipe 61 may be broken, and in the case of closed circuit steam cooling, the leakage amount of the cooling steam to the combustion gas also increases. There is an upper limit for the difference. Therefore, when the allowable pressure difference is C, the pressure P ₃ and the pressure P ₄ are given by
The relational expression shown by is established.

[Equation 3] C> P ₃ −P ₄ > 0 Furthermore, the temperature T ₃ of the gas turbine high temperature section 24 is measured by the third temperature measuring device 68, and the temperature T ₃ is compared with the allowable temperature T, The comparison result is sent to the valve opening / closing control device 74.

The temperature T ₃ of the gas turbine high temperature section 24 should not exceed the allowable temperature T due to the material problem of the gas turbine high temperature section 24. Therefore, the temperature T ₃
And the allowable temperature T, the relational expression shown by the following equation 4 is established.

Equation 4 T−T ₃ > 0 From this, it is understood that the pressure P ₃ of the cooling steam and the temperature T ₃ of the gas turbine high temperature portion 24 must be maintained at appropriate values.

Therefore, when the compressor rotation speed control device 73 takes in the pressure P _{3 of the} cooling steam and the pressure P _{4 of the} combustion gas and the pressure difference becomes equal to or more than the allowable pressure difference C in the pressure relational expression. Sends a command to the compressor driving device 63 to reduce the number of rotations of the vapor compressor 62 and reduce the pressure P ₃ . On the contrary, when the pressure difference between the pressures P ₃ and P ₄ approaches 0, the rotation speed of the steam compressor 62 is increased by a command from the compressor rotation speed control device 73 to the compressor drive device 63. Increase the pressure P ₃ . By the above control, the pressure P ₃ of the cooling steam can be maintained at an appropriate value.

Normally, the temperature T _{3 of the} high temperature part 24 of the gas turbine is
Is maintained at an appropriate value by opening / closing the bypass valve 65 via the valve opening / closing controller 74 and adjusting the flow rate of the cooling steam through the bypass 64. However, if TT ₃ <0 in the temperature relational expression, the temperature T ₃ of the gas turbine high temperature portion 24 exceeds the allowable temperature T. Therefore, in response to a command from the valve opening / closing control device 74, the valve 72 provided in the water spray pipe 70 is opened, and the cooling steam exiting the steam compressor 62 is pressurized with the feed water taken from the feed system of the steam turbine system 60. The pressure is raised by the pump 71, and water is sprayed through the water spray pipe 70 to reduce the temperature of the cooling steam until the temperature reaches the allowable temperature T. By the above control, the temperature T ₃ of the high temperature part 24 of the gas turbine is set to the allowable temperature T _3.
Can be housed within.

Therefore, according to this ninth embodiment,
Gas turbine high temperature part 24 extracted from the steam turbine system 60
The temperature and pressure of the cooling steam to be supplied to the gas turbine high temperature part 2 can be adjusted and supplied to an appropriate value.
It is possible to keep the temperature and pressure of No. 4 appropriate and to operate the plant stably.

[0119]

The present invention described above has the following effects.

(Claim 1) According to the invention of claim 1, a steam compressor for boosting steam is installed in the cooling steam piping system, and the heat recovery cooling after cooling the high temperature part of the gas turbine is carried out. By compressing the steam with the steam compressor, the steam conditions (temperature and pressure) of the heat recovery cooling steam in the steam turbine system can be matched, and the cooling steam to be supplied to the high temperature part of the gas turbine can be By compressing with the steam compressor, the cooling steam is pressurized to a pressure equal to or higher than the combustion gas pressure of the gas turbine device, and stable cooling steam can be supplied to the high temperature portion of the gas turbine. There is an effect that the plant can be operated in a stable state by cooling and accurately collecting the heat recovery cooling steam after cooling.

(Claim 2) According to the invention of claim 2 of the present invention, the steam compressor is installed in the cooling steam supply pipe for supplying the cooling steam to the high temperature part of the gas turbine. By compressing the cooling steam, the supply pressure of the cooling steam to the high temperature part of the gas turbine can be constantly increased to a pressure higher than the pressure of the combustion gas of the gas turbine.
Eliminates problems such as high temperature combustion gas entering the gap of the gas turbine, raising the temperature of the member in the gap, or mixing combustion gas with the cooling steam that obstructs the operation of the cooling steam supply and recovery system. There are possible effects.

(Claim 3) According to the invention of claim 3 of the present invention, a steam compressor is installed in the heat recovery cooling steam discharge pipe for recovering the heat recovery cooling steam after cooling the high temperature part of the gas turbine. When the cooling steam after heat recovery in the high temperature part of the gas turbine is mixed and recovered in the steam turbine system, the heat recovery cooling steam is compressed by the steam compressor, and the temperature of the cooling steam is increased to raise the pressure of the steam compressor. It has the effect that the heat recovery cooling steam can be mixed with the steam conditions (temperature and pressure) of the recovery destination, and the driving force required for the steam compressor is converted into an increase in sensible heat of the steam. There is an effect that it can be operated efficiently.

(Claim 4) According to the invention of claim 4 of the present invention, the vapor compressor is installed in the cooling vapor supply pipe and the vapor compressor is also installed in the heat recovery cooling vapor discharge pipe. By compressing the cooling steam with the steam compressor installed in the cooling steam supply pipe, the cooling steam can be constantly boosted to a pressure higher than the pressure of the combustion gas of the gas turbine. Has the effect of being able to supply stable cooling steam to the high temperature part of the gas turbine, and the heat recovery cooling steam after cooling the high temperature part of the gas turbine with the steam compressor installed in the heat recovery cooling steam discharge pipe. By compressing, increasing the temperature and increasing the pressure, the steam conditions (temperature and pressure) of the steam compressor can be made to match the steam conditions (temperature and pressure) of the heat recovery cooling steam mixed and recovered. Because, the heat recovery cooling steam is effective it can be recovered smoothly steam turbine system.

(Claim 5) According to the invention of claim 5 of the present invention, since the steam compressor is drivingly connected to the gas turbine device or the steam turbine system, the entire plant including the steam compressor is compact. There is an effect that can be summarized in
Compared to the case where the electric power generated by the generator of the combined plant is used as the driving force of the vapor compressor, there is an effect that the operating cost of the vapor compressor can be reduced.

(Claim 6) According to the invention of claim 6 of the present invention, a steam turbine is connected to the steam compressor as a driving device of the steam compressor, and the driving force of the steam turbine is generated in the plant. Since low-pressure steam is used, there is an effect that the efficiency of the generator can be improved compared to the case where the electric power generated by the generator of the combined plant is used as the driving force of the steam compressor, and it is supplied to the steam turbine. Since the rotation speed can be adjusted only by changing the flow rate of steam to be generated, there is an effect that the rotation speed of the steam compressor can be easily controlled.

(Claim 7) According to the invention of claim 7, the water supplied from the steam turbine system is supplied between the steam compressor installed in the cooling steam supply pipe and the inlet of the high temperature part of the gas turbine. Since the cooling steam temperature adjusting means for adjusting the temperature of the cooling steam by utilizing it is additionally provided, there is an effect that the temperature of the cooling steam supplied to the high temperature part of the gas turbine can be easily adjusted to an appropriate value.

(Claim 8) According to the invention of claim 8, the steam turbine system is provided with a confluent portion of the mainstream steam and the heat recovery cooling steam, and an outlet of the high temperature portion of the gas turbine and the confluent portion are provided. Connected by a heat recovery cooling steam discharge pipe, a steam compressor is installed in the heat recovery cooling steam discharge pipe, and steam temperature adjusting means for adjusting the temperature of the mainstream steam and the heat recovery cooling steam toward the confluence part, and A steam pressure adjusting means for adjusting the pressure of the heat recovery cooling steam toward the merging portion is provided,
The heat recovery cooling steam is compressed by the steam compressor, and after the pressure is increased, the pressure of the heat recovery cooling steam toward the merging portion is adjusted by the steam pressure adjusting means. It can always be adjusted to an appropriate value and sent to the merging section, and the heat recovery cooling steam is compressed by the vapor compressor to raise the temperature, and then the temperatures of the mainstream steam and the heat recovery cooling steam toward the merging section are adjusted. Since the temperature is adjusted by the steam temperature adjusting means, the temperatures of the mainstream steam and the heat recovery cooling steam can be adjusted to appropriate values and sent to the merging portion, so that the heat recovery cooling to the steam turbine system is performed through the merging portion. There is an effect that steam can be recovered in an appropriate state.

(Claim 9) According to the invention of claim 9 of the present invention, the cooling steam extraction section and the inlet of the high temperature section of the gas turbine are connected by a cooling steam supply tube, and steam is connected to this cooling steam supply tube. A compressor is installed, and further, steam temperature adjusting means for adjusting the temperature of the cooling steam from the steam compressor toward the high temperature part of the gas turbine, steam pressure adjusting means for adjusting the pressure of the cooling steam, and flow rate of the cooling steam. It is possible to compress the cooling steam by the steam compressor to increase the pressure, and then to adjust the pressure of the cooling steam to an appropriate value by the steam pressure adjusting means and send it out. Further, the temperature of the cooling steam can be adjusted to an appropriate value and sent out by the steam temperature adjusting means, and the flow rate of the cooling steam can be adjusted to an appropriate value and sent out by the steam flow rate adjusting means. That result, the effect of suitability pressure to the gas turbine hot section, the temperature and flow rate the cooling steam supply may be cooled.

[Brief description of drawings]

FIG. 1 is a system diagram showing a first embodiment of the present invention.

FIG. 2 is a system diagram showing a second embodiment of the present invention.

FIG. 3 is a system diagram showing a third embodiment of the present invention.

FIG. 4 is a system diagram showing a fourth embodiment of the present invention.

FIG. 5 is a system diagram showing a fifth embodiment of the present invention.

FIG. 6 is a system diagram showing a sixth embodiment of the present invention.

FIG. 7 is a system diagram showing a seventh embodiment of the present invention.

FIG. 8 is a system diagram showing an eighth embodiment of the present invention.

FIG. 9 is a system diagram showing a ninth embodiment of the present invention.

[Explanation of symbols]

1 ... Air compressor of gas turbine device, 2 ... Combustor, 3
… The same gas turbine, 4… Generator, 5… Exhaust heat recovery boiler,
6 ... Low-pressure drum of exhaust heat recovery boiler, 7 ... Medium-pressure drum,
8 ... same high-pressure drum, 15 ... same superheater, 16 ... same reheater,
19 ... High-pressure steam turbine of steam turbine system, 20 ... Reheat steam turbine, 21 ... Low-pressure steam turbine, 22 ... Condenser, 23 ... Water supply pump, 108 ... Water supply pipe, 24 ...
High temperature part of gas turbine, 25 ... Steam compressor of heat recovery cooling steam, 26 ... Compressor drive device, 107 ... Cooling steam supply pipe,
110 ... Heat recovery cooling steam discharge pipe, 109 ... Water spray pipe of cooling steam temperature adjusting means, 27 ... Same pressure pump, 28 ...
Cooling steam vapor compressor, 29 ... Compressor drive device, 201
… Cooling steam supply pipe connecting between the low pressure drum and the inlet of the cooling steam vapor compressor, 202 ... Heat recovery cooling steam discharge pipe connecting between the outlet of the heat recovery cooling steam vapor compressor and the high pressure steam turbine, 32 ... Cooling steam , A steam turbine for driving the steam compressor of the steam turbine, 203 ... A steam supply pipe connecting between the low-pressure drum and the inlet of the steam turbine, 204 ... A steam return pipe connecting between the outlet of the steam turbine and the upstream pipe of the condenser, … Steam compressor for heat recovery cooling steam, 205… Heat recovery cooling steam discharge pipe connecting the outlet of the high temperature part of the gas turbine and the inlet of the steam compressor, 206
… Heat recovery cooling steam return pipe that connects between the outlet of the steam compressor and the reheater, 40 ... Steam turbine system, 41 ... Gas turbine high temperature section, 42 ... Cooling steam supply pipe, 43 ... Mainstream steam and heat recovery cooling steam Confluence part, 44 ... Heat recovery cooling steam discharge pipe, 45 ...
Heat recovery cooling steam vapor compressor, 46 ... Compressor drive device,
47 ... Water supply system of steam turbine system, 48, 49 ... First and second water spray pipes constituting steam temperature adjusting means, 5
0, 51 ... First and second pressurizing pumps, 52, 53 ... First and second valves, 54, 55 ... First and second temperature measuring devices, 58 ... Valve opening / closing control device , 56, 57 ...
First and second pressure measuring devices constituting steam pressure adjusting means, 59 ... Compressor rotation speed control device, 60 ... Steam turbine system, 61 ... Cooling steam supply pipe, 62 ... Cooling steam steam compressor , 63 ... Compressor drive device, 64 ... Bypass of cooling steam which constitutes cooling steam flow rate adjusting means, 65 ... The same bypass valve, 66, 67 ... Third and fourth which constitutes cooling steam pressure adjusting means Pressure measuring device, 73 ... Compressor rotation speed control device, 68 ... Temperature measuring device that constitutes cooling steam temperature adjusting means, 69 ... Allowable temperature setting device, 70 ... Water spray pipe, 71 ... Addition Pressure pump, 72 ... Same valve, 7
4 ... Valve opening / closing control device.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Shinichi Hoizumi 3-1-1, Saiwai-cho, Hitachi-shi, Ibaraki Hitachi Ltd. Hitachi factory (72) Inventor Toshihiko Sasaki 3-chome, Saiwai-cho, Hitachi-shi, Ibaraki 1-1 Hitachi Ltd., Hitachi Works, Hitachi Plant (72) Inventor Yoshiki Noguchi 3-1-1, Saiwaicho, Hitachi City, Ibaraki Hitachi Ltd., Hitachi Works, Hitachi Plant (72) Inventor Shozo Nakamura Tsuchiura, Ibaraki Prefecture 502 Kantachimachi

Claims (9)

[Claims] 1. A steam cooling gas turbine power plant using cooling steam as a cooling medium for cooling a high temperature part of a gas turbine, wherein a steam compressor for boosting the pressure of steam is installed in a cooling steam piping system. Cooling gas turbine power plant. 2. In a steam-cooled gas turbine power plant that uses cooling steam as a cooling medium for cooling the high temperature portion of the gas turbine, a steam compressor is provided in a cooling steam supply pipe for supplying cooling steam to the high temperature portion of the gas turbine. A steam-cooled gas turbine power plant characterized by being installed. 3. A steam recovery gas turbine power plant that uses cooling steam as a cooling medium for cooling the high temperature part of the gas turbine, and heat recovery cooling steam discharge for recovering the heat recovery cooling steam after cooling the high temperature part of the gas turbine. A steam-cooled gas turbine power plant characterized in that a steam compressor is installed in the pipe. 4. In a steam cooling gas turbine power plant that uses cooling steam as a cooling medium for cooling a high temperature part of a gas turbine, a steam compressor is provided in a cooling steam supply pipe for supplying cooling steam to the high temperature part of the gas turbine. A steam-cooled gas turbine power plant, wherein a steam compressor is installed in a heat recovery cooling steam discharge pipe for recovering the heat recovery cooling steam after cooling the high temperature part of the gas turbine. 5. The steam-cooled gas turbine power plant according to claim 1, wherein the steam compressor is drivingly connected to either a gas turbine device or a steam turbine system. 6. A low-pressure steam generated in a plant is used as a driving force of the steam turbine, the steam turbine being connected to the steam compressor as a drive device thereof. The steam-cooled gas turbine power plant according to any one of claims. 7. A cooling steam temperature adjusting means for adjusting the temperature of the cooling steam by using the feed water from the steam turbine system between the steam compressor installed in the cooling steam supply pipe and the inlet of the high temperature part of the gas turbine. The steam-cooled gas turbine power plant according to claim 2 or 3, further comprising: 8. A steam-cooled gas turbine power plant for supplying steam as a cooling medium to the high temperature part of the gas turbine, cooling the high temperature part of the gas turbine with the cooling steam, and recovering the recovered heat recovery cooling steam to the steam turbine system. In the above, the steam turbine system is provided with a merging portion of the mainstream steam and the heat recovery cooling steam, and the outlet of the high temperature portion of the gas turbine and the merging portion are connected by a heat recovery cooling steam discharge pipe. A steam compressor is installed in the steam compressor, steam temperature adjusting means for adjusting the temperatures of the mainstream steam and the heat recovery cooling steam toward the merging portion, and steam pressure adjusting means for adjusting the pressure of the heat recovery cooling steam toward the merging portion. A steam-cooled gas turbine power plant characterized by being provided with. 9. In a steam-cooled gas turbine power plant that uses cooling steam as a cooling medium for cooling the high temperature part of the gas turbine, a cooling steam supply pipe is connected between the extraction part of the cooling steam and the inlet of the high temperature part of the gas turbine. Then, a steam compressor is installed in this cooling steam supply pipe, and steam temperature adjusting means for adjusting the temperature of the cooling steam from the steam compressor to the high temperature part of the gas turbine, and a steam pressure for adjusting the pressure of the cooling steam. A steam-cooled gas turbine power plant, comprising: adjusting means; and steam flow rate adjusting means for adjusting the flow rate of the cooling steam.