JPH0476205A - Combined cycle electric power plant - Google Patents

Abstract

PURPOSE:To finely collect heat from a gas turbine system so as to improve heat efficiency by providing a heat exchanger being made to carry out the heat exchange between an exhaust gas flowing to a waste heat recovery boiler from the gas turbine and the high pressurized air being supplied from a compressor. CONSTITUTION:A combined cycle electric power plant comprising a gas turbine system 1 composed of a gas turbine 10, a generator 11 and a compressor 12, a combustor 13 and a regenerative unit 14 which is a heat exchanger, and a steam turbine system 2 composed of a steam turbine 23, a generator 24, a condenser 25 for returning completely expanded steam by passing through the steam turbine 23 to the cold water, a steam generating unit 26 for reheating this cold water, producing high pressure steam, and supplying it to the steam turbine 23. In this case, the heat exchanger 14 is provided to carry out the heat exchange between waste gas flowing to a waste heat recovery boiler 27 of the steam generating unit 26 from the gas turbine and high pressurized air being supplied from the compressor. The heat efficiency of the plant can be greatly improved thereby.

Description

[Detailed Description of the Invention] [Purpose of the Invention (Industrial Application Field) The present invention combines a gas turbine system and a steam turbine system that recovers exhaust heat from the gas turbine system to drive a steam turbine. related to combined cycle power generation plants.

(Prior Art) Recently, there has been a strong desire to improve the efficiency of thermal power plants. In order to meet this demand, combined cycle systems are being promoted not only in newly constructed thermal power plants but also in existing thermal power plants.

In a combined cycle power plant, fuel is usually introduced into a combustor together with high-pressure air sent out from a compressor and combusted, and the high-temperature, high-pressure gas obtained from this combustion is used to drive a gas carbine for driving a generator. The system consists of a gas turbine system and a steam turbine system in which the exhaust gas of the gas turbine system is passed through an exhaust heat recovery boiler to generate steam, and this steam drives a steam turbine for driving a generator. In such combined cycle power plants, a method is adopted in which the temperature of the gas at the inlet of the gas turbine is increased in order to further improve thermal efficiency.

However, in conventional combined cycle power plants,
In particular, since it does not adopt a configuration that finely recovers heat from the gas turbine system, the thermal efficiency is at most 40% based on LHV standards.
There were some problems as low as %.

(Problems to be Solved by the Invention) As described above, conventional combined cycle power plants have a problem of low thermal efficiency because they do not perform detailed heat recovery.

Therefore, an object of the present invention is to provide a combined cycle power generation plant that can finely recover heat from a gas turbine system, thereby significantly improving thermal efficiency.

[Configuration of the Invention (Means for Solving the Problem) In order to achieve the above object, according to an embodiment of the present invention, fuel is introduced into the combustor together with high pressure air sent out from the compressor. The gas turbine system uses the high-temperature, high-pressure gas obtained from this combustion to drive a gas carbine for driving a generator, and the exhaust gas from this gas turbine system is passed through an exhaust heat recovery boiler to generate steam. In a combined cycle power generation plant comprising a steam turbine system that drives a steam turbine for driving a generator, the exhaust gas flowing from the gas turbine to the exhaust heat recovery boiler and the high pressure air sent out from the compressor It is equipped with a heat exchanger that performs heat exchange.

(Function) High-pressure air sent out from the compressor is heated by exhaust gas from the gas turbine via a heat exchanger, becomes even hotter, and is sent to the combustor. Therefore, when obtaining high-temperature, high-pressure gas at a certain temperature in the combustor, the amount of fuel required to obtain high-temperature, high-pressure gas at that temperature can be reduced. Also,
Conversely, if the amount of fuel supplied is kept constant, the temperature of the high-temperature, high-pressure gas obtained in the combustor can be further increased, thereby making it possible to increase the circularity of the gas turbine system. Therefore, it is possible to improve thermal efficiency compared to conventional plants.

(Example) Examples will be described below with reference to the drawings.

FIG. 1 shows a system diagram of a combined cycle power plant according to an embodiment of the present invention.

This plant is comprised of a gas turbine system 1 and a steam turbine system 2 that is driven using the exhaust heat of the gas turbine system 1 as an energy source.

The gas turbine system 1 includes a gas turbine 1o, a generator 11 and a compressor 12 driven by the gas turbine 10, a combustor 13, and a regenerator 14 that is a heat exchanger.

The compressor 12 compresses the room temperature air guided through the path 15. High-pressure air sent out from the compressor 12 is guided to the combustor 13 via a path 16, a secondary path 17 of the regenerator 14, and a path 18.

Fuel is supplied to the combustor 13 from a fuel supply system (not shown), and the fuel or high-pressure air is used as a combustion supporting gas to burn the fuel.

The high temperature gas obtained by combustion is supplied to the gas turbine 10 via the path 19, expanded and
After applying a driving force to , it flows to path 20 . In this example, high-temperature, high-pressure gas at 1400° C. flows into the gas turbine 10, and exhaust gas whose temperature has decreased to 600° C. flows out from the gas turbine 10.

Exhaust gas discharged from the gas turbine 10 is routed through a path 20,
It is guided to the steam turbine system 2, which will be described next, via the primary side path 21 and path 22 of the regenerator 14 in this order.

The steam turbine system 2 includes a steam turbine 23, a generator 24 driven by the steam turbine 23, a condenser 25 that returns steam that has passed through the steam turbine 23 and has been completely expanded to room temperature water, and a The steam generator 26 generates high-pressure steam by heating the room-temperature water returned by the steam generator 25 again and supplies the high-pressure steam to the steam turbine 23.

The steam generator 26 mainly includes an exhaust heat recovery boiler 27 that recovers heat from the exhaust gas guided through the path 22 of the gas turbine system 1 described above. Exhaust heat recovery boiler 2
Reference numeral 7 is composed of a one-pressure boiler equipped with only a high-pressure section A. The exhaust heat recovery boiler 27 includes a high-pressure heater 28, a high-pressure evaporator 29, and a high-pressure preheater 30 along the flow direction of the exhaust gas.
is provided.

The room temperature water returned by the condenser 25 is supplied to the high-pressure preheater 30 via a path 31. The water that has passed through this high-pressure preheater 30 is transferred to a high-pressure drum 32, a circulation pump 33, and a high-pressure evaporator 2.
9, it passes through the high-pressure drum 32 and the high-pressure heater 28 and becomes high-pressure steam. This high-pressure steam is supplied to the steam turbine 23 through the path 34 and is used to drive the steam turbine 23.

With such a configuration, the high-pressure air sent out from the compressor 12 is heated by the exhaust gas of the gas turbine 10 via the regenerator 14, becomes even hotter, and is sent to the combustor 13. Therefore, when obtaining high-temperature gas at a certain temperature in the combustor 13, the amount of fuel required to obtain high-temperature gas at that temperature can be reduced. Furthermore, when the amount of fuel supplied is kept constant, the temperature of the high-temperature gas obtained in the combustor can be increased, thereby increasing the output of the gas turbine 10.

Therefore, thermal efficiency can be improved compared to conventional plants.

In this embodiment, if a pressurizing pump 35 is added between the high-pressure drum 32 and the high-pressure heater 28, as shown by the two-dot chain line in FIG.
The saturation temperature at No. 2 can be lowered, and the pinch point temperature difference can be prevented from becoming smaller.

Furthermore, as shown by the two-dot chain line in the figure, if steam can be introduced into the combustor 13 from the path 34 via the flow rate regulating valve 36, the flow rate of the gas turbine 10 can be increased, thereby increasing the gas flow rate. Since the output of the turbine 10 can be increased, the steam turbine system 2 can be downsized.

FIG. 2 shows a system diagram of a combined cycle power plant according to another embodiment of the present invention. In this figure, the same parts as in FIG. 1 are designated by the same reference numerals. Therefore, detailed explanation of the overlapping parts will be omitted.

The difference between the plant according to this embodiment and the one shown in FIG. 1 is that the compressors are a low pressure compressor 12a and a high pressure compressor 12b.
The compressed air from the low pressure compressor 12a is guided to the high pressure compressor 12b through the primary side of the heat exchanger 37.

Then, the room temperature water returned by the condenser 25 is passed through the path 38.
, is led to the secondary side of the heat exchanger 37 via a high-pressure pump 39, and the room temperature water that has passed through this secondary side is led to the high-pressure preheater 30 via a path 40.

With such a configuration, not only the same effects as the embodiment shown in FIG. 1 can be obtained, but also the low pressure compressor 12
Since the heat retained in the compressed air emitted from the steam turbine system 2a can be recovered by the heat exchanger 37, and the recovered heat can be used in the steam turbine system 2a, it is possible to further improve the layer thermal efficiency. In this case, the temperature of the compressed air flowing into the high-pressure compressor 12b can be lowered, and as a result, the compression work of the entire compressor' can be reduced.

In this embodiment, as shown by the two-dot chain line in the figure, the pinch void temperature difference can be increased and the gas The output of the turbine 10 can be increased.

FIG. 3 shows a system diagram of a combined cycle power plant according to yet another embodiment of the present invention.

In this figure, the same parts as in FIGS. 1 and 2 are designated by the same reference numerals. Therefore, detailed explanation of the overlapping parts will be omitted.

The difference between the plant according to this embodiment and the one shown in FIGS. 1 and 2 is that the compressor has a three-stage configuration of a low pressure compressor 12c, an intermediate pressure compressor 12d, and a high pressure compressor 12e, and the low pressure compressor The compressed air coming out from the heat exchanger 37a is guided to the medium pressure compressor 12d via the primary side of the heat exchanger 37a, and the medium pressure compressor 1
The compressed air exiting from the heat exchanger 37b is guided to the high pressure compressor 37b via the primary side of the heat exchanger 37b.

Then, the room temperature water returned by the condenser 25 is transferred to the route 3.
8. Direct the room-temperature water that has passed through the secondary side of the heat exchanger 37a to the secondary side of the heat exchanger 37a via the high-pressure pump 39 and guide it to the high-pressure preheater 30 via the secondary side of the heat exchanger 37b and the path 40. I have to.

With such a configuration, the thermal efficiency can be improved as in the embodiment shown in FIG. 2, and the compression work of the entire compressor can be effectively reduced.

FIG. 4 shows a system diagram of a combined cycle power plant according to yet another embodiment of the present invention.

In this figure, the same parts as in FIG. 2 are designated by the same reference numerals. Therefore, detailed explanation of the overlapping parts will be omitted.

The plant according to this embodiment differs from the plant shown in FIG. 2 in the configuration of the steam generator 26a.

The steam generator 26a is connected to the path 22 of the gas turbine system IC.
The main body is an exhaust heat recovery boiler 27a that recovers heat from the exhaust gas guided through the exhaust gas.

The exhaust heat recovery boiler 27a is composed of a two-pressure boiler including a high pressure section A and a low pressure section B. The high-pressure part A is provided with a high-pressure heater 28, a high-pressure evaporator 29, and a high-pressure preheater 30 along the flow direction of exhaust gas, and the low-pressure part B is provided with a low-pressure heater 41, a low-pressure An evaporator 42 and a low pressure preheater 43 are provided.

On the one hand, the room temperature water returned by the condenser 25 is routed to route 3.
8. Water is supplied to the high-pressure preheater 30 via the flow rate adjustment valve 44, the high-pressure pump 39, the secondary side of the heat exchanger 37, and the path 40. The water that has passed through the high-pressure preheater 30 is transported to a high-pressure drum 32,
It passes through the circulation pump 33, high-pressure evaporator 29, high-pressure drum 32, and high-pressure heater 28, and becomes high-pressure steam. This high-pressure steam is supplied to the high-pressure inlet of the steam turbine 23 through the path 34 and is used to drive the steam turbine 23.

On the other hand, the room temperature water returned by the condenser 25 is supplied to the low pressure preheater 43 via the low pressure pump 45.

The water that has passed through the low-pressure preheater 43 passes through the low-pressure drum 46, circulation pump 47, low-pressure evaporator 42, low-pressure drum 46, and low-pressure heater 41, and becomes low-pressure steam. This low-pressure steam is supplied to the low-pressure inlet of the steam turbine 23 through a path 48 and is used to drive the steam turbine 23.

With such a configuration, the same effects as in each of the above embodiments can be obtained, and the thermal efficiency can be improved by preventing a decrease in the pinch point temperature difference and increasing the amount of heat recovered in the steam L-bin system 2c. can be further improved.

In this embodiment, as shown by the two-dot chain line in the figure, a pressurizing pump 35 is added between the high-pressure drum 32 and the high-pressure heater 28, or flow rate regulating valves 36a, 36b are connected from the paths 34, 48. By allowing steam to be introduced into the combustor co-3 via the combustor co-3, the pinch void temperature difference can be increased and the output of the gas turbine IO can be increased.

FIG. 5 shows a system diagram of a combined cycle power plant according to a different embodiment of the present invention. In this figure, the same parts as in FIG. 4 are designated by the same reference numerals. Therefore, detailed explanation of the overlapping parts will be omitted.

The plant according to this embodiment is different from the one shown in FIG.
The compressed air coming out of the medium pressure compressor 12d is guided to the medium pressure compressor 12d via the primary side of the heat exchanger 37a, and the compressed air leaving the medium pressure compressor 12d is guided to the high pressure compressor 3 via the primary side of the heat exchanger 37b.
I'm trying to lead you to 7e.

A part of the room temperature water returned by the condenser 25 is guided to the secondary side of the heat exchanger 37a via the path 38, the flow rate adjustment valve 44, and the high pressure pump 39, and the room temperature water that has passed through the secondary side is guided to the secondary side of the heat exchanger 37a. is led to the high-pressure preheater 30 via the secondary side of the heat exchanger 37b and the path 40.

With such a configuration, it is possible to obtain the same effects as in the embodiment described above, and also to transfer the heat retained in the compressed air from the low pressure compressor 12c and the intermediate pressure compressor 12d to the heat exchanger 37a. , 37b, and the recovered heat can be used in the steam turbine system 2d, which further improves the layer thermal efficiency. Also in this case, the temperature of the compressed air flowing into the high-pressure compressor 12d can be lowered, so that the compression work of the entire compressor can be reduced as a result.

FIG. 6 shows a system diagram of a combined cycle power plant according to yet another embodiment of the present invention. In this figure, the same parts as in FIG. 4 are designated by the same reference numerals. Therefore, detailed explanation of the overlapping parts will be omitted.

The plant according to this embodiment differs from the plant shown in FIG. 4 in the configuration of the steam generator 26c.

The steam generator 26C is connected to the path 22 of the gas turbine system 1e.
The main body is an exhaust heat recovery boiler 27b that recovers heat from the exhaust gas guided through the exhaust gas.

The exhaust heat recovery boiler 27b is composed of a three-pressure boiler including a high pressure section A, an intermediate pressure section B, and a low pressure section C.

In the high pressure section A, a high pressure heater 28 is installed along the flow direction of the exhaust gas.
, a high-pressure evaporator 29 are provided, and the intermediate-pressure section B includes an intermediate-pressure heater 50 and an intermediate-pressure evaporator 51 along the flow direction of the exhaust gas.
, a medium-pressure preheater 52 are provided, and the low-pressure section C is further provided with a low-pressure heater 53, a low-pressure evaporator 54, and a low-pressure preheater 55 along the flow direction of the exhaust gas.

On the one hand, the room temperature water returned from the condenser 25 is routed through route 3.
8. Water is supplied to the intermediate pressure preheater 52 via the flow rate adjustment valve 44, the high pressure pump 39, the secondary side of the heat exchanger 37, and the path 40. The water that has passed through this medium pressure preheater 52 is transferred to a medium pressure drum 56,
Circulation pump 57, medium pressure evaporator 51, medium pressure drum 56, pressure pump 58, medium pressure heater 50. It passes through the high-pressure drum 32, circulation pump 33, high-pressure evaporator 29, high-pressure drum 32, and high-pressure heater 28, and becomes high-pressure steam. This high-pressure steam is supplied to the high-pressure inlet of the steam turbine 23 through the path 34 and is used to drive the steam turbine 23.

On the other hand, the room temperature water returned by the condenser 25 is supplied to the low pressure preheater 55 via the low pressure pump 45.

The water that has passed through this low-pressure preheater 55 passes through a low-pressure drum 59, a circulation pump 60, a low-pressure evaporator 54, a low-pressure drum 59, and a low-pressure heater 53, and becomes low-pressure steam. This low-pressure steam is supplied to the low-pressure inlet of the steam turbine 23 through a path 48 and is used to drive the steam turbine 23.

With such a configuration, the same effects as in each of the embodiments described above can be obtained, and the amount of heat recovered in the steam turbine system 2e can be increased, so that the thermal efficiency can be further improved.

FIG. 7 shows a system diagram of a combined cycle power plant according to yet another embodiment of the present invention.

In this figure, the same parts as in FIG. 6 are indicated by the same reference numerals. Therefore, a detailed explanation of the overlapping parts will be omitted.

The plant according to this embodiment differs from the plant shown in FIG. 6 in the configuration of the steam generator 26d.

The steam generator 26d is connected to the path 22 of the gas turbine system 1f.
The main body is an exhaust heat recovery boiler 27C that recovers heat from the exhaust gas guided through the exhaust gas.

The exhaust heat recovery boiler 27c is composed of a three-pressure boiler in which a high pressure section A, a middle and low pressure section B', and a low pressure section C are visible.

In the high pressure section A, a high pressure heater 28 is installed along the flow direction of the exhaust gas.
, a high-pressure evaporator 29, and a high-pressure preheater 30,
In the medium and low pressure section B', there is a medium and low pressure heater 61 along the flow direction of the exhaust gas. A medium and low pressure evaporator 62 and a medium and low pressure preheater 63 are provided, and the low pressure section C is further provided with a low pressure evaporator 54 and a low pressure preheater 55 along the flow direction of the exhaust gas.

On the one hand, the room temperature water returned by the condenser 25 is routed to route 3.
8. Water is supplied to the high-pressure preheater 30 via the flow rate adjustment valve 44, the high-pressure pump 39, the secondary side of the heat exchanger 37, and the path 40. The water that has passed through this high-pressure preheater 30 is transported to a high-pressure tram 32,
It passes through the circulation pump 33, high-pressure evaporator 29, high-pressure drum 32, and high-pressure heater 28, and becomes high-pressure steam. This high-pressure steam is supplied to the high-pressure inlet of the steam turbine 23 through the path 34 and is used to drive the steam turbine 23.

On the other hand, the room temperature water returned by the condenser 25 is supplied to the low pressure preheater 55 via the low pressure pump 45.

The water that has passed through the low pressure preheater 55 is transferred to a low pressure drum 59, a circulation pump 60, a low pressure evaporator 54, a low pressure drum 59, a pressurizing pump 64, a medium and low pressure preheater 63, a medium and low pressure drum 65, a circulation pump 66, a medium and low pressure evaporator 62, medium and low pressure drum 65,
It passes through the medium and low pressure heater 61 and becomes medium and low pressure steam. This medium and low pressure steam is supplied to the low pressure inlet of the steam turbine 23 through a path 48 and is used to drive the steam turbine 23.

Even with this configuration, it is possible to obtain the same effects as in the above embodiment.

FIG. 8 shows a system diagram of a combined cycle power plant according to yet another embodiment of the present invention.

In this figure, the same parts as in FIG. 2 are designated by the same reference numerals. Therefore, a detailed explanation of the overlapping parts will be omitted.

This embodiment differs from the embodiment shown in FIG. 2 in that a regenerator for exchanging heat between the exhaust gas of the gas turbine 10 and the high-pressure air exiting the compressor is omitted. That is, in this embodiment, the amount of heat recovered by the heat exchanger 37 provided between the low-pressure compressor 12a and the high-pressure compressor 12b and the amount of heat recovered from the exhaust gas of the gas turbine 10 via the waste heat recovery boiler 27 are The generated heat is used to drive the steam turbine system 2a.

Even with such a configuration, thermal efficiency can be improved compared to conventional plants.

FIG. 9 shows a system diagram of a combined cycle power plant according to yet another embodiment of the present invention. In this figure, the same parts as in FIG. 3 are designated by the same reference numerals. Therefore, a detailed explanation of the overlapping parts will be omitted.

This embodiment differs from the embodiment shown in FIG. 3 in that a regenerator for exchanging heat between the exhaust gas of the gas turbine 10 and the high-pressure air exiting the compressor is omitted. That is, in this embodiment, the amount of heat recovered by the heat exchangers 37a and 37b provided between the low-pressure compressor 12c and the intermediate-pressure compressor 12d and between the intermediate-pressure compressor 12d and the high-pressure compressor 12e, respectively. The amount of heat recovered from the exhaust gas of the gas turbine 10 via the exhaust heat recovery boiler 27 drives the steam turbine system 2b.

Even with this configuration, thermal efficiency can be improved compared to conventional plants.

FIG. 10 shows a system diagram of a combined cycle power plant according to yet another embodiment of the present invention. In this figure, the same parts as in FIG. 4 are designated by the same reference numerals. Therefore, detailed explanation of the overlapping parts will be omitted.

This embodiment differs from the embodiment shown in FIG. 4 in that a regenerator for exchanging heat between the exhaust gas of the gas turbine 10 and the high-pressure air exiting the compressor is omitted. That is, in this embodiment, the amount of heat recovered by the heat exchanger 37 provided between the low pressure compressor 12a and the high pressure compressor 12b, and the amount of heat recovered from the exhaust gas of the gas turbine 10 via the waste heat recovery boiler 27a. The generated heat is used to drive the steam turbine system 2C.

FIG. 11 shows the temperature of each part in the exhaust heat recovery boiler 27a shown in FIG. 10.

Even with this configuration, sufficient effects can be obtained.

FIG. 12 shows a system diagram of a combined cycle power plant according to a different embodiment of the present invention.

In this figure, the same parts as in FIG. 5 are designated by the same reference numerals. Therefore, detailed explanation of the overlapping parts will be omitted.

This embodiment differs from the embodiment shown in FIG. 5 in that a regenerator for exchanging heat between the exhaust gas of the gas turbine 10 and the high-pressure air exiting the compressor is omitted. That is, in this embodiment, the amount of heat recovered by the heat exchangers 37a and 37b provided between the low pressure compressor 12C and the intermediate pressure compressor 12d and between the intermediate pressure compressor 12d and the high pressure compressor 12e, respectively. The amount of heat recovered from the exhaust gas of the gas turbine 10 via the exhaust heat recovery boiler 27a drives the steam turbine system 2d.

This configuration is also effective.

FIG. 13 shows a system diagram of a combined cycle power plant according to a different embodiment of the present invention.

In this figure, the same parts as in FIG. 6 are indicated by the same reference numerals. Therefore, detailed explanation of the overlapping parts will be omitted.

This embodiment differs from the embodiment shown in FIG. 6 in that a regenerator for exchanging heat between the exhaust gas of the gas turbine 10 and the high-pressure air exiting the compressor is omitted. That is, in this embodiment, the amount of heat recovered by the heat exchanger 37 provided between the low-pressure compressor], 2a and the high-pressure compressor 12b and the exhaust gas of the gas turbine 10 via the waste heat recovery boiler 27b are The steam turbine system 2e is driven by the amount of heat recovered from the steam turbine.

It may be configured in this way.

FIG. 14 shows a system diagram of a combined cycle power plant according to yet another embodiment of the present invention. In this figure, the same parts as in FIG. 7 are designated by the same reference numerals. Therefore, detailed explanation of the overlapping parts will be omitted.

This embodiment differs from the embodiment shown in FIG. 7 in that a regenerator for exchanging heat between the exhaust gas of the gas turbine 10 and the high-pressure air exiting the compressor is omitted. That is, in this embodiment, the amount of heat recovered by the heat exchanger 37 provided between the low pressure compressor 12a and the high pressure compressor 12b and the amount of heat recovered from the exhaust gas of the gas turbine 10 via the waste heat recovery boiler 27c are used. The generated heat is used to drive the steam turbine system 2f.

This configuration is also effective.

Note that the present invention is not limited to the embodiments described above. In other words, it is not limited to cases in which each side is implemented independently;
Combinations of one or more can also be implemented.

[Effects of the Invention] As detailed above, according to the present invention, compared to conventional combined cycle power plants, heat can be recovered from the gas turbine system more precisely, thereby improving thermal efficiency, and improving the steam turbine system. It can also contribute to downsizing.

[Brief explanation of drawings]

FIG. 1 is a system diagram of a combined cycle power plant according to an embodiment of the present invention, FIGS. 2 to 10 are system diagrams showing combined cycle power plants according to different embodiments of the present invention, and FIG. 10 is a diagram showing an example of the temperature of each part in the exhaust heat recovery boiler in the embodiment shown in FIG.
14 are system diagrams showing combined cycle power plants according to further different embodiments of the present invention. 1, la, lb, lc, ld, le, If. Ig, lh, li, lj, lk, 1g...Gas turbine system, 2.2a, 2b, 2c, 2d, 2e2f...
Steam turbine system,] 0... Gas turbine, 11- Generator, 12... Compressor, 12a, 12c... Low pressure compressor, 12b, 12e... High pressure compressor, 12d... Medium pressure compressor , 13... combustor, 14... regenerator, 23.
... Steam turbine, 24... Generator, 25... Condenser, I d... Steam generator, 27° 27 b. ...Exhaust heat recovery boiler, 37°b...Heat exchanger.

Claims (3)

[Claims] (1) A gas turbine system in which fuel is introduced into a combustor together with high-pressure air sent out from a compressor and combusted, and the high-temperature and high-pressure gas obtained by this combustion drives a gas carbine for driving a generator; A combined cycle power generation plant comprising a steam turbine system that passes the exhaust gas of the gas turbine system through an exhaust heat recovery boiler to generate steam, and uses this steam to drive a steam turbine for driving a generator. A combined cycle power generation plant characterized by comprising a heat exchanger that performs heat exchange between the exhaust gas flowing to the exhaust heat recovery boiler and the high pressure air sent out from the compressor. (2) a gas turbine system in which fuel is introduced into a combustor together with high-pressure air sent out from a compressor and combusted, and the high-temperature, high-pressure gas obtained by this combustion drives a gas carbine for driving a generator; The high-pressure air is obtained in a combined cycle power generation plant equipped with a steam turbine system in which the exhaust gas of the gas turbine system is passed through an exhaust heat recovery boiler to generate steam, and the steam is used to drive a steam turbine for driving a generator. For this purpose, a plurality of compressors are provided in a multi-stage configuration, and a heat exchanger that performs heat exchange between compressed air passing between these compressors and water used for steam generation in the steam turbine system. A combined cycle power generation plant characterized by: (3) a gas turbine system in which fuel is introduced into a combustor together with high-pressure air sent out from a compressor and combusted, and the high-temperature, high-pressure gas obtained by this combustion drives a gas carbine for driving a generator; The high-pressure air is obtained in a combined cycle power generation plant equipped with a steam turbine system in which the exhaust gas of the gas turbine system is passed through an exhaust heat recovery boiler to generate steam, and the steam is used to drive a steam turbine for driving a generator. A first heat exchanger for performing heat exchange between a plurality of compressors provided in a multi-stage configuration for the purpose of the present invention, compressed air passing between these compressors, and water used for steam generation in the steam turbine system. and a second heat exchanger that performs heat exchange between the exhaust gas flowing from the gas turbine to the exhaust heat recovery boiler and the high-pressure air sent out from the compressor located at the final stage. A combined cycle power generation plant characterized by: