JP2001214758A - Gas turbine combined power generation plant facility - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gas turbine combined power generation facility in which the temperature control of steam generated in a heat exchanger for cooling the compressed air of a closed air-cooled gas turbine is simplified. SOLUTION: The compressed air of the closed air-cooled gas turbine is successively cooled by the heat exchangers divided into at least a plurality of pieces of an evaporator 4 and a preheater 5, and the saturated steam generated in the evaporator 4 is included in the saturated steam generated from an exhaust heat recovery boiler 11.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a gas turbine combined cycle power plant facility.

[0002]

2. Description of the Related Art In recent years, in order to improve the efficiency of a gas turbine, the temperature of the gas turbine has been increased to, for example, a combustion temperature exceeding 1500 ° C. As the temperature of the gas turbine rises, it becomes necessary to cool high-temperature components such as turbine blades. One of the cooling methods is to temporarily cool part of the air compressed by the compressor with a heat exchanger. A closed air-cooled gas turbine has been proposed in which air that has been introduced into a gas turbine, cools blades and the like inside the gas turbine, and has risen in temperature again is collected and mixed directly into a combustor.

[0003] As a closed air cooling gas turbine, for example, a technique described in Japanese Patent Application Laid-Open No. H11-182263 has been proposed, in which water or steam of a steam cycle is used as a cooling medium for cooling compressed air. A device provided with a utilized heat exchanger is described. This heat exchanger includes a superheater that superheats steam in a high temperature range and a preheater that heats water in a low temperature range. The steam generated in the evaporator of the exhaust heat recovery boiler is supplied to the superheater, and the superheated steam is recovered in the middle of the superheater of the exhaust heat recovery boiler. Further, a part of the water supply to the exhaust heat recovery boiler is supplied to the preheater, and the heated water is recovered to the outlet of the economizer of the exhaust heat recovery boiler.

[0004]

SUMMARY OF THE INVENTION The above-mentioned Japanese Patent Application Laid-Open No.
In the gas turbine combined cycle power plant described in Japanese Patent No. 182263, when returning the steam superheated by the superheater to the exhaust heat recovery boiler, the steam temperature is adjusted to the temperature at the mixing point in order to ensure the characteristics of the boiler and the soundness of the material. Must be approached. In particular, when the temperature characteristics of the exhaust gas of the gas turbine and the temperature characteristics of the compressed air fluctuate, such as when starting the gas turbine, a measuring device, a control device, a control valve, and the like for measuring the steam conditions in order to adjust the steam temperature. Is required, and the equipment and the operation method are complicated. On the other hand, the number of parts is increased, so that the reliability and the economic efficiency may be reduced.

The present invention has been made in view of the above-mentioned problems of the prior art, and has as its object to provide a gas turbine in which the temperature control of steam generated in a heat exchanger for cooling compressed air is simplified. An object of the present invention is to provide a combined power generation facility.

[0006]

In order to solve the above-mentioned object, a gas turbine combined cycle power plant of the present invention comprises a compressor for compressing air, and a combustion for burning compressed air and fuel guided from the compressor. A gas turbine driven by combustion gas burned in the combustor, and a part of compressed air from the compressor is supplied to a gas turbine cooling unit, and the compressed air passing through the cooling unit is supplied to the combustor. Gas turbine cooling system, exhaust heat recovery boiler for recovering exhaust heat from gas turbine exhaust gas, steam turbine driven by steam generated by the exhaust heat recovery boiler, and supplying water to the exhaust heat recovery boiler And a part of compressed air branched from the compressor to a gas turbine cooling system and a part of water supplied from the water supply system. And heat exchange between the evaporator, which cools the compressed air to evaporate the feed water, the feed water guided to the exhaust heat recovery boiler, and the compressed air that has passed through the evaporator, and exchanges the compressed air. A preheater for further cooling and heating the feedwater of the water supply system; and a path for supplying steam generated by the evaporator to saturated steam generated by the exhaust heat recovery boiler is provided. .

Also, a compressor for compressing air, a combustor for burning compressed air and fuel guided from the compressor, a gas turbine driven by combustion gas burned in the combustor, Gas turbine cooling system for supplying a part of the compressed air from the gas turbine to a gas turbine cooling unit and supplying the compressed air passing through the cooling unit to the combustor, and an exhaust heat recovery boiler for recovering exhaust heat from gas turbine exhaust gas And a steam turbine driven by steam generated in the exhaust heat recovery boiler, and a water supply system for supplying water to the exhaust heat recovery boiler. A first heat exchanger for exchanging heat with a part of the compressed air branched into the water supply and a part of the feedwater branched from the water supply system; and the water supply system guided to the exhaust heat recovery boiler. And a second heat exchanger that exchanges heat with the compressed air that has passed through the first heat exchanger,
A path for supplying steam generated by heat exchange with the compressed air in the first heat exchanger to saturated steam generated in the exhaust heat recovery boiler is provided.

[0008]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a configuration diagram of a gas turbine combined cycle power plant showing an embodiment of the present invention.

The gas turbine combined cycle power plant shown in FIG.
It can be broadly divided into gas turbine systems, steam turbine systems, water supply systems, and gas turbine air cooling systems.

First, the gas turbine system will be described.
The gas turbine includes a compressor 1, a combustor 2, and a turbine 3
And a gas turbine generator 9 mechanically connected to the gas turbine. In the gas turbine system, the air 7 is compressed by the compressor 1, and a part of the compressed air is introduced into the combustor 2. In the combustor 2, combustion gas is generated by mixing with the fuel and burning. The combustion gas is guided from the combustor 2 to the turbine 3 and drives the turbine 3. The shaft power generated by the gas turbine is transmitted to the gas turbine generator 9 and converted into electric energy. The exhaust heat recovery from the gas turbine exhaust gas is performed by the exhaust heat recovery boiler 11, which will be described later, on the gas turbine exhaust gas 8 whose work has been completed in the turbine 3.

The exhaust heat recovery boiler 11 includes a low pressure economizer 12,
Low-pressure evaporator 13, high-pressure evaporators 14, 15, high-pressure superheater 1
6, a low-pressure drum 17 and a high-pressure drum 18. The high-temperature gas turbine exhaust gas 8 guided to the exhaust heat recovery boiler 11 is first subjected to exhaust heat recovery by high-pressure evaporators 14 and 15 connected to a high-pressure drum 18, and heats feed water to generate high-pressure steam. The high-pressure steam generated by heating in the high-pressure evaporators 14 and 15 is guided from the high-pressure drum 18 to the superheater 16, further heated by the superheater 16, and then supplied to the steam turbine 22 through the high-pressure steam pipe 19. . In the low-pressure evaporator 13, the high-pressure evaporator 1 described above is used.
Exhaust heat recovery is performed from the gas turbine exhaust gas that has passed through the gas turbines 4 and 15. The low-pressure superheated steam generated in the low-pressure evaporator 13 is supplied to the steam turbine 22 via the low-pressure steam pipe 20 connected to the low-pressure drum 17 in the middle stage.

Next, the steam turbine system will be described. The steam turbine equipment includes a steam turbine 22 driven by steam generated by the exhaust heat recovery boiler, a condenser 23 for condensing steam that has completed work in the steam turbine 22, and a steam turbine generator driven by the steam turbine to generate power. 2
1 is provided. A high-pressure steam pipe 19 to which high-pressure steam is supplied and a low-pressure steam pipe 20 to which low-pressure steam is supplied are connected to the high-pressure drum 18 and the low-pressure drum of the exhaust heat recovery boiler described above. The steam turbine is driven by steam supplied via the high-pressure steam pipe 19 and the low-pressure steam pipe 20.

Next, the water supply system will be described. The water supply system shown in this embodiment includes a condensate pump 27 for increasing the condensate guided from the condenser, and a water supply supplied from the condensate pump.
(Condensed water), a preheater 5, a deaerator 29 for deaerated water supplied through the preheater 5, and a water supply pump 30 for supplying the deaerated water to the exhaust heat recovery boiler 11. And Further, in the present embodiment, a bypass valve is provided for bypassing the water supply from the middle of the path for guiding the water supply from the condensate pump 27 to the preheater 5 to the middle of the path for guiding the water supply through the preheater 5 to the deaerator 29. Configuration. In addition, steam required for deaeration of feedwater is supplied to the deaerator 29 by a deaerated steam supply pipe 31 which is a path branched from the middle of the low-pressure steam pipe 20. A part of the water supplied from the water supply pump 30 to the exhaust heat recovery boiler 11 is supplied to an evaporator 4 described later.

Next, a gas turbine air cooling system will be described. In the gas turbine air cooling system of the present embodiment,
An evaporator is provided as a first heat exchanger, and a preheater 5 is provided as a second heat exchanger. The cooling air that has passed through the evaporator 4 and the preheater 5 is supplied to the gas turbine cooling unit by the booster 6. A part of the compressed air is supplied from the compressor 1 to the air cooling system, and after the compressed air is cooled by the evaporator 4 and the preheater 5, a cooling path (not shown) is used for cooling gas turbine blades and the like. . The air that has passed through the cooling section of the gas turbine is mixed into the combustor 2. As described above, in the present embodiment, a gas turbine combined cycle power plant including a closed air-cooled gas turbine is applied. The details will be described below.

A part of the compressed air compressed by the compressor 1 and led to the combustor 2 is first supplied to the evaporator 4 as gas turbine cooling air. Further, a part of the water supplied from the water supply system to the evaporator 4 is, for example, in the present embodiment shown in FIG.
As described above, a part of the water supplied from the deaerator 29 to the exhaust heat recovery boiler 11 via the water supply pump is supplied as a cooling medium for the compressed air. Since the temperature of the compressed air from the compressor 1 is high, it is necessary to lower the temperature. The evaporator 4 exchanges heat between the compressed air and a part of the water supplied through the deaerator 29 to cool the compressed air. Is performed.

On the other hand, the feedwater supplied to the evaporator 4 generates steam by performing heat exchange with high-temperature compressed air.
The steam generated in the evaporator 4 is supplied to the low-pressure steam pipe 20 via the steam supply pipe 10. At this time, the evaporator 4, the steam supply pipe 10, the low-pressure drum 17, and the low-pressure steam pipe 20 are each in a pressure-balanced state, and the steam conditions generated by the evaporator 4 are saturated because the steam conditions are saturated. No significant temperature difference occurs between the temperature and the temperature of the steam generated in the low-pressure drum 17. Therefore, the steam generated from the evaporator 4 can be mixed with the steam generated from the exhaust heat recovery boiler 11 (low-pressure drum 17) without requiring a complicated temperature control device. It is possible to suppress the thermal fatigue of the structural material. Further, since the complicated temperature control device can be omitted, the operation of the plant can be simplified, and the reliability of the equipment can be improved.

The compressed air cooled by the evaporator 4 is supplied to a preheater 5. Further, the preheater 5 is supplied with water supplied from the condenser 23 to the deaerator 29 as a cooling medium of the compressed air. The compressed air supplied to the preheater 4 exchanges heat with water in a water supply system, so that the air temperature is further cooled. The air cooled by the preheater 5 is pressurized by the booster 6 and supplied to the cooling section of the gas turbine. The cooling air whose temperature has increased through the gas turbine cooling unit is mixed into the combustor 2 and used as combustion air. On the other hand, the supply water at the outlet of the condensate pump 27 supplied to the preheater 5 is heated by exchanging heat with air for cooling the gas turbine. Preheater 5
Is supplied to the deaerator 29.

In the present embodiment shown in FIG. 1, a preheater bypass valve 28 and a preheater bypass path 44 are provided in the middle of the path for guiding water supply from the condenser 23 (condensate pump 27) to the preheater 5. The configuration is as follows. The preheater bypass path 44 is connected in the middle of a path that guides the water supplied through the preheater 5 to the deaerator 29, and controls the amount of water supplied to the preheater 5 via this bypass path. That is, in this embodiment, in order to control the temperature of the compressed air to a temperature required for cooling the gas turbine, if the temperature of the compressed air is too low, the amount of bypass of the preheater 5 is increased to increase the amount of the preheater 5. Control is performed to reduce the flow rate flowing through the inside of the preheater 5 and reduce the amount of exchanged heat in the preheater 5.

The temperature of the feedwater supplied to the preheater 5 is increased by heat exchange with the compressed air. The feedwater passed through the preheater 5 is supplied to the deaerator 29,
As described above, since the deaerator supply water temperature is increased, the flow rate of the deaerated steam required for deaeration can be reduced. In the steam cycle shown in FIG.
The degassed steam is supplied through a degassed steam supply pipe 31 branched from the low-pressure steam pipe 20. Therefore, since the low-pressure steam flowing into the steam turbine 22 is increased by reducing the flow rate of the degassed steam, it is possible to increase the electric power that can be generated by the steam turbine generator 21.

Although FIG. 1 shows an embodiment in which the evaporator 4 and the preheater 5 are formed as separate structures, the evaporator 4 and the preheater 5 are formed as an integral structure, The same effect can be obtained even when the structure is such that the air flows through the evaporator 4 and the preheater 5 sequentially. Further, in the gas turbine cooling system of the present embodiment, the compressed air is
Although cooling is performed in the order of the preheater 5, it is also possible to perform cooling in the order of the preheater 5 and the evaporator 4. further,
It is also possible to install the evaporator 4 and the preheater 5 in parallel in the gas turbine cooling system to cool the compressed air.

In the present embodiment described above, one of the heat exchangers for cooling the compressed air is the evaporator 4, and the generated steam is mixed with the steam generated from the evaporator (low-pressure drum 17) of the exhaust heat recovery boiler 11. The configuration is such that Since the evaporator 4 for cooling the compressed air and the evaporator (low-pressure drum 17) of the exhaust heat recovery boiler 11 are connected by the steam supply pipe 10, the pressures of the respective evaporators are balanced. Also,
Since both evaporators generate saturated steam, the saturated steam temperature is almost the same, so that fine temperature adjustment is not required.

As described above, according to the present embodiment, complicated temperature control is required when the steam recovered from the compressed air of the closed air cooling gas turbine and recovered in heat is mixed into the steam cycle of the exhaust heat recovery boiler 11 and the steam turbine 22. It is possible to eliminate the temperature difference between the steam on the exhaust heat recovery boiler side and the steam generated by the gas turbine air cooling heat exchanger (evaporator 4) without installing equipment or requiring fine temperature adjustment. it can. Therefore, it is possible to provide a gas turbine combined cycle power generation system which is simple in operation method, has excellent reliability because no complicated control equipment is required, and has excellent economical efficiency because of a small number of parts.

In this embodiment, the preheater bypass valve 2
8, the amount of water supplied to the preheater 5 can be adjusted, so that the temperature of the compressed air can be controlled to a temperature required for cooling the gas turbine.

FIG. 2 is a configuration diagram of a gas turbine combined cycle power plant showing another embodiment of the present invention. In the following description, the description of the same configuration as in FIG. 1 will be omitted.

In this embodiment, the compressed air is bypassed from the middle of the path for guiding the compressed air from the compressor 1 to the evaporator 4 to the middle of the path for guiding the compressed air from the preheater 5 to the booster 6. The air bypass duct 34 is provided. The compressed air bypass duct 34 is provided with a compressed air bypass flow rate adjusting device 33 for adjusting the flow rate of air flowing through the duct. With the above-described configuration, a part of the compressed air at the outlet of the compressor 1 is supplied to the evaporator 4 and the preheater 5 by the compressed air bypass duct 34.
It can flow into the booster 6 without passing through.

That is, in this embodiment, when it is necessary to adjust the temperature of the compressed air at the inlet of the booster 6, the compressor 1
By branching a part of the compressed air compressed by the above and mixing it into the compressed air at the inlet of the booster 6 without passing through the evaporator 4 and the preheater 5, the temperature of the cooling air supplied to the gas turbine can be adjusted. Become. If the temperature of the compressed air at the inlet of the booster becomes higher than the required value of the gas turbine, the evaporator 4
In addition, the flow rate bypassing the preheater 5 is reduced, and the flow rate cooled in the evaporator 4 and the preheater 5 is increased to lower the compressed air temperature.

Although FIG. 2 shows a facility for adjusting the temperature of the compressed air at the inlet of the booster 6 by bypassing both the evaporator 4 and the preheater 5, only the evaporator 4 or
It is also possible to adjust the temperature of the compressed air at the inlet of the booster 6 by providing a path that bypasses only the preheater 5.

FIG. 3 is a configuration diagram of a gas turbine combined cycle power plant showing another embodiment of the present invention.

In the example shown in FIG. 3, in order to adjust the temperature of the compressed air at the inlet of the booster 6, a thermometer 39 is installed in the middle of the path in which the compressed air flows from the preheater 5 to the booster 6, and a thermometer 39 is provided. The amount of water flowing through the preheater 5 is adjusted based on the temperature measured at 39. In this configuration, if the temperature of the compressed air is too low, the preheater bypass valve is operated to increase the amount of water that bypasses the preheater and reduce the amount of heat exchanged in the preheater. The same effect can be obtained when the thermometer 39 is installed on the outlet side of the booster 6.

A high-pressure steam turbine bypass pipe 37 and a high-pressure steam turbine bypass valve 38 are installed in the high-pressure steam pipe 19 so that the generated high-pressure steam can flow into the condenser 23 without passing through the steam turbine 22. Become.

A low-pressure steam turbine bypass pipe 35 and a low-pressure steam turbine bypass valve 36 are installed in the low-pressure steam pipe 20 so that the generated low-pressure steam can flow into the condenser 23 without passing through the steam turbine 22. Become.

When the plant is started, the gas turbine is started first, but the compressed air needs to be cooled in order to operate the closed air-cooled gas turbine. Therefore, cooling water is supplied to the preheater 5 using the condensing pump 27. At this time, a preheater circulation pipe 25 and a preheater circulation amount adjusting valve 24 are installed so that a part of water heated by cooling the compressed air can be recovered in the condenser 23. Further, at a stage where the conditions of the steam cycle are not established at the time of start-up, there is no method for recovering the steam generated in the evaporator 4, and therefore the condenser 2 is provided by the low-pressure steam turbine bypass pipe 35 and the low-pressure steam turbine bypass valve 36.
3 so that it can be collected. When the gas turbine enters a normal operation state and the temperature of the exhaust gas of the gas turbine rises and the steam generated in the exhaust heat recovery boiler 11 is established, the high-pressure steam turbine bypass valve 38 and the low-pressure steam turbine bypass valve 36 are closed. Steam is introduced into the steam turbine 22. By performing the above operation, it is possible to operate the closed air-cooled gas turbine in a wide range.

FIG. 4 is a configuration diagram of a gas turbine combined cycle power plant showing still another embodiment.

In this embodiment shown in FIG. 4, a thermometer 39 is provided at a position where the air temperature of the compressed air after the compressed air bypassing the evaporator 4 and the preheater 5 is joined can be measured. . The bypass amount of the compressed air can be adjusted based on the temperature measured by the thermometer 39.

FIG. 5 is a block diagram of a gas turbine combined cycle power plant showing still another embodiment.

In this embodiment, in order to control the temperature of the compressed air for cooling at the inlet of the turbine 3, part of the air at the outlet of the booster 6 is compressed via the compressed air recirculation duct 43 at the outlet of the compressor 1. It is configured to join the air. Thermometer 3
Reference numeral 9 denotes a booster 6 outlet side, which is installed downstream of the branch point with the compressed air recirculation duct 43 and installed in the compressed air recirculation duct 43 based on the measured temperature of the compressed air for cooling at the turbine inlet. The compressed air recirculation amount is controlled by the operation of the compressed air recirculation flow rate adjusting device 42 thus performed.

By controlling the amount of recirculation of the compressed air, it is possible to control the temperature of the compressed air at the turbine 3 inlet. For example, when the temperature of the compressed air for cooling at the inlet of the turbine 3 is high, the amount of compressed air recirculation is increased by the operation of the compressed air recirculation flow rate adjusting device 42 to decrease the temperature of the compressed air for cooling. When the temperature of the compressed air for cooling is low, control is performed to decrease the amount of recirculated compressed air and increase the temperature of the compressed air for cooling.

FIG. 6 is a block diagram of a gas turbine combined cycle power plant showing still another embodiment.

In this embodiment, a low-pressure steam turbine inlet valve 40 for adjusting the low-pressure steam pressure and the like is installed in the low-pressure steam supply pipe 20 for supplying the steam generated from the exhaust heat recovery boiler 11 to the steam turbine 22. . The low-pressure steam turbine inlet valve 40 controls the pressure of the low-pressure steam and the like based on the temperature of the compressed air measured by a thermometer provided between the preheater 5 and the booster 6.

Here, when the temperature of the compressed air is low,
By controlling the valve at the steam turbine inlet,
The internal pressure of the evaporator 4 and the low-pressure drum 17 increases. Since the amount of evaporation decreases as the internal pressure increases, the amount of heat exchanged in the evaporator 4 decreases. Therefore, the temperature of the compressed air at the outlet of the evaporator 4 increases. On the other hand, when the temperature of the compressed air is high, by opening the valve at the inlet of the steam turbine, the amount of heat exchanged in the evaporator 4 can be increased to lower the temperature of the compressed air.

FIG. 7 is a block diagram of a gas turbine combined cycle power plant showing still another embodiment.

In this embodiment shown in FIG. 7, the steam generated in the evaporator 4 is mixed with the steam generated from the high-pressure drum 18. In order to mix the high-pressure steam with the high-pressure steam, the water supply at the outlet of the deaerator is pressurized by the pressurizing pump 41 and supplied to the evaporator 4. When mixed with high-pressure steam, the amount of high-pressure steam increases, so that the amount of work in the steam turbine increases as compared with the case of mixing with low-pressure steam, and it becomes possible to obtain more electric output.

Further, as in the case of mixing into the low-pressure steam shown in FIGS. 1 to 6, since it mixes with the saturated steam from the drum, fine temperature adjustment by pressure balance is not required.

In the embodiment shown in FIGS. 1 to 7, several examples are shown as means for controlling the temperature of the compressed air for cooling at the inlet of the turbine 3, but the same applies to the case where a plurality of means are combined. It is possible to control the temperature of the compressed air for cooling. For example, by controlling the bypass flow rate of the condensate preheater 5 while controlling the recirculation amount of the cooling compressed air, it is possible to more efficiently adjust the temperature of the compressed air.

In the embodiment shown in FIGS. 1 to 7, the steam cycle is mainly described as a non-reheating double pressure.
Even in the case of a reheating cycle or a single-pressure or triple-pressure cycle configuration, the compressed air of the closed air-cooled gas turbine is sequentially cooled by a heat exchanger divided into at least a plurality of evaporators and preheaters, and evaporated. Saturated steam generated in the evaporator and the exhaust heat recovery boiler drum, etc., do not require fine control devices and adjustments by mixing the saturated steam generated in the evaporator with the saturated steam generated from the exhaust heat recovery boiler. It is possible to eliminate the temperature difference from the saturated steam generated in the above, and it is possible to ensure the soundness of the piping material.

According to the embodiment shown in FIGS. 1 to 7, the heat transfer area of the gas turbine air cooler using the evaporator and the preheater is the same as that of the conventional superheater having the same performance. The total heat transfer area can be reduced to about 2/3 as compared with a gas turbine air cooler using a heat exchanger, and as a result, the size of the heat exchanger can be reduced and the cost can be reduced. In addition to the above, there is an effect that the arrangement area can be reduced, and carrying-in and installation become easy.

[0047]

According to the present invention, it is possible to provide a gas turbine combined cycle power generation facility in which the temperature control of steam generated in a heat exchanger for cooling compressed air is simplified.

[Brief description of the drawings]

FIG. 1 is a system configuration diagram of a power plant showing one embodiment of the present invention.

FIG. 2 is a system configuration diagram of a power plant showing one embodiment of the present invention.

FIG. 3 is a system configuration diagram of a power plant showing one embodiment of the present invention.

FIG. 4 is a system configuration diagram of a power plant showing one embodiment of the present invention.

FIG. 5 is a system configuration diagram of a power plant showing one embodiment of the present invention.

FIG. 6 is a system configuration diagram of a power plant showing one embodiment of the present invention.

FIG. 7 is a system configuration diagram of a power plant showing one embodiment of the present invention.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Compressor, 2 ... Combustor, 3 ... Turbine, 4 ... Evaporator,
5 preheater, 6 booster, 7 air, 8 gas turbine exhaust, 9 gas turbine generator, 10 steam supply piping,
11: Exhaust heat recovery boiler, 12: Low pressure economizer, 13: Low pressure evaporator, 14: High pressure economizer, 15: High pressure evaporator, 16 ...
High-pressure super heater, 17: low-pressure drum, 18: high-pressure drum, 1
9 ... High-pressure steam pipe, 20 ... Low-pressure steam pipe, 21 ... Steam turbine generator, 22 ... Steam turbine, 23 ... Condenser, 2
4 ... Preheater circulation amount control valve, 25 ... Preheater circulation pipe, 26
... make-up water pipe, 27 ... condensate pump, 28 ... preheater bypass valve, 29 ... deaerator, 30 ... boiler feed pump, 31 ...
Deaerated steam supply pipe, 32 ... Boiler feedwater pipe, 33 ... Compressed air bypass flow rate adjusting device, 34 ... Compressed air bypass duct, 35 ... Low pressure steam turbine bypass pipe, 36 ... Low pressure steam turbine bypass valve, 37 ... High pressure steam turbine bypass Piping, 38 ... high-pressure steam turbine bypass valve, 39
... thermometer, 40 ... low-pressure steam turbine inlet valve, 41 ... booster pump, 42 ... compressed air recirculation flow control device, 43 ... compressed air recirculation duct, 44 ... preheater bypass path.

Claims (9)

[Claims] A compressor for compressing air; a combustor for burning fuel and compressed air guided from the compressor; a gas turbine driven by combustion gas burned in the combustor; Gas turbine cooling system for supplying a part of the compressed air from the gas turbine to a gas turbine cooling unit and supplying the compressed air passing through the cooling unit to the combustor, and an exhaust heat recovery boiler for recovering exhaust heat from gas turbine exhaust gas And a steam turbine driven by steam generated in the exhaust heat recovery boiler, and a water supply system for supplying water to the exhaust heat recovery boiler. Heat exchange between a part of the compressed air branched into the water supply and a part of the supply water branched from the water supply system, and an evaporator for cooling the compressed air to evaporate the water supply; Water supply to the boiler,
A preheater that exchanges heat with the compressed air that has passed through the evaporator, further cools the compressed air, and heats the water in the water supply system, and the steam generated in the evaporator is generated in the exhaust heat recovery boiler. Gas turbine combined cycle power plant equipment provided with a path for supplying saturated steam. 2. A compressor for compressing air, a combustor for burning compressed air and fuel guided from the compressor, a gas turbine driven by combustion gas burned in the combustor, Gas turbine cooling system for supplying a part of the compressed air from the gas turbine to a gas turbine cooling unit and supplying the compressed air passing through the cooling unit to the combustor, and an exhaust heat recovery boiler for recovering exhaust heat from gas turbine exhaust gas And a steam turbine driven by steam generated by the waste heat recovery boiler, a condenser for condensing steam passed through the steam turbine, and supplying water supplied from the condenser to the waste heat recovery boiler In the gas turbine combined cycle power plant equipment having a water supply system and a deaerator installed in the water supply system to deaerate the water supply, a part of the compressed air branched from the compressor to a gas turbine cooling system, An evaporator for exchanging heat with a part of the feedwater guided to the exhaust heat recovery boiler through the deaerator and cooling the compressed air to evaporate the feedwater; a compressed air passing through the evaporator; A heat exchanger for exchanging heat with the feedwater guided to the air blower, further cooling the compressed air and heating the feedwater of the water supply system, and in the course of supplying steam from the exhaust heat recovery boiler to the steam turbine. A gas turbine combined cycle power plant facility, wherein a path for supplying steam generated in the evaporator is provided. 3. A compressor for compressing air, a combustor for combusting compressed air and fuel guided from the compressor, a gas turbine driven by combustion gas burned in the combustor, Gas turbine cooling system for supplying a part of the compressed air from the gas turbine to a gas turbine cooling unit and supplying the compressed air passing through the cooling unit to the combustor, and an exhaust heat recovery boiler for recovering exhaust heat from gas turbine exhaust gas And a steam turbine driven by steam generated in the exhaust heat recovery boiler, and a water supply system for supplying water to the exhaust heat recovery boiler. A preheater for exchanging heat between a part of the compressed air branched into the water and feedwater guided to the exhaust heat recovery boiler, cooling the compressed air and heating the feedwater of the water supply system, and the preheater And evaporator that exchanges heat between the compressed air that has passed through and a part of the feedwater branched from the water supply system, and further cools the compressed air to evaporate the feedwater.The evaporator generates steam generated by the evaporator. Gas turbine combined cycle power plant equipment provided with a path for supplying saturated steam generated in an exhaust heat recovery boiler. 4. A compressor for compressing air, a combustor for burning compressed air and fuel guided from the compressor, a gas turbine driven by combustion gas burned in the combustor, Gas turbine cooling system for supplying a part of the compressed air from the gas turbine to a gas turbine cooling unit and supplying the compressed air passing through the cooling unit to the combustor, and an exhaust heat recovery boiler for recovering exhaust heat from gas turbine exhaust gas And a steam turbine driven by steam generated in the exhaust heat recovery boiler, and a water supply system for supplying water to the exhaust heat recovery boiler. An evaporator for exchanging heat between a part of the compressed air branched into the water supply and a part of the feed water branched from the water supply system, cooling the compressed air to evaporate the water supply, and A part of the compressed air branched to the bin cooling system, and heat exchange between the feedwater guided to the exhaust heat recovery boiler, a preheater that cools the compressed air and heats the feedwater of the feedwater system, A gas turbine combined cycle power plant facility comprising a path for supplying steam generated by the evaporator to saturated steam generated by the exhaust heat recovery boiler. 5. A measuring device for measuring the temperature of the compressed air is provided in the middle of a path for guiding the compressed air from the preheater to the gas turbine cooling section, and a measuring device is provided for the preheater in accordance with the temperature of the compressed air. The gas turbine combined cycle power plant equipment according to claim 1 or 2, further comprising a control device for controlling an amount of supplied water. 6. A measuring device for measuring the temperature of the compressed air is provided in the middle of a path for guiding the compressed air from the preheater to the gas turbine cooling section, and the evaporator or the evaporator is provided in accordance with the temperature of the compressed air. The gas turbine combined cycle plant equipment according to claim 1 or 2, further comprising a control device that controls a flow rate of the compressed air supplied to the preheater. 7. A measuring device for measuring a temperature of the compressed air passing through the evaporator is provided, and a flow rate of steam generated by the evaporator to be supplied to the steam turbine is controlled according to a temperature of the compressed air. The gas turbine combined cycle power plant equipment according to claim 1 or 2, wherein a control device is provided at the steam turbine inlet. 8. A compressor for compressing air, a combustor for burning compressed air and fuel guided from the compressor, a gas turbine driven by combustion gas burned in the combustor, Gas turbine cooling system for supplying a part of the compressed air from the gas turbine to a gas turbine cooling unit and supplying the compressed air passing through the cooling unit to the combustor, and an exhaust heat recovery boiler for recovering exhaust heat from gas turbine exhaust gas And a steam turbine driven by steam generated in the exhaust heat recovery boiler, and a water supply system for supplying water to the exhaust heat recovery boiler. A first heat exchanger for exchanging heat with a part of the compressed air branched into the water supply and a part of the feedwater branched from the water supply system; and a water supply system of the water supply system led to the exhaust heat recovery boiler. And a second heat exchanger for exchanging heat with the compressed air that has passed through the first heat exchanger, and the steam generated by heat exchange with the compressed air in the first heat exchanger is generated by the exhaust heat recovery. Gas turbine combined cycle power plant equipment provided with a path for supplying saturated steam generated in a boiler. 9. A compressor for compressing air, a combustor for burning compressed air and fuel guided from the compressor, a gas turbine driven by combustion gas burned in the combustor, and a gas turbine. A water supply system having an exhaust heat recovery boiler that recovers exhaust heat from exhaust gas to generate steam, and a steam turbine driven by the steam generated by the exhaust heat recovery boiler, and supplies water to the exhaust heat recovery boiler In the gas turbine combined cycle power plant equipment in which a deaerator is installed, a part of the compressed air that is branched from the compressor to the combustor and a feedwater guided from the deaerator to an exhaust heat recovery boiler A first heat exchanger for exchanging heat with a part thereof, heat exchange between compressed air passing through the first heat exchanger, and feed water guided to the deaerator, and cooling the compressed air with a gas turbine. Second to the combustor via the section A heat exchanger, and a path for supplying steam generated by heat exchange with the compressed air in the first heat exchanger to saturated steam generated in the exhaust heat recovery boiler. Power plant equipment.