Gas turbine plant, its operation method, and its modification method

Abstract

This gas turbine plant comprises a gas turbine, a liquefaction facility capable of liquefying air, and a liquefaction controller for controlling the liquefaction facility. A compressor has an intake amount adjuster capable of adjusting an intake amount into a compressor casing. The liquefaction facility comprises: a bleed line capable of bleeding compressed air from the compressor; a liquefaction system capable of liquefying the compressed air; a bleed amount adjustment valve capable of adjusting a flow rate of the compressed air; a return air line capable of guiding return air, which is air obtained through vaporization of liquid air, into a flow passage through which compressed air flows in the gas turbine; and a return amount adjusting valve capable of adjusting a flow rate of the return air. The liquefaction controller opens the bleed amount adjustment valve if an opening degree of the intake amount adjuster is a first opening degree, and opens the return amount adjusting valve if the opening degree of the intake amount adjuster is a second opening degree, which is an opening degree greater than the first opening degree.

Description

[Technical field]

[0001] The present disclosure relates to a gas turbine plant including a gas turbine, a method for operating the same, and a method for modifying the same. This application claims priority based on Patent Application No. 2021-192907, filed in Japan on November 29, 2021, the contents of which are incorporated herein by reference. [Background technology]

[0002] A gas turbine includes a compressor that compresses air, a combustor that burns fuel in the air compressed by the compressor to generate combustion gas, and a turbine that is driven by the combustion gas.

[0003] The following Patent Document 1 discloses a technique for increasing gas turbine output. In this technique, air compressed by a compressor is liquefied by a liquefaction device, and this liquefied air, that is, liquid air, is stored in a tank. Then, during peak load of the gas turbine, the liquid air in the tank is heated and vaporized, and this air is introduced into the combustor. With this technique, during peak load of the gas turbine, in addition to air from the compressor, vaporized air from the liquid air is introduced into the combustor, so that the gas turbine output during peak load of the gas turbine can be increased. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Patent Application Publication No. 50-153120 Summary of the Invention [Problem to be solved by the invention]

[0005] Operators of gas turbine plants are required to vary the gas turbine output in response to load fluctuations in the power system, and therefore it is desirable to be able to flexibly adjust the gas turbine output.

[0006] Therefore, an object of the present disclosure is to provide a technique that enables gas turbine output adjustment to be flexibly performed. [Means for solving the problem]

[0007] A gas turbine plant as one embodiment for achieving the above object comprises: The gas turbine includes a compressor capable of compressing air, a combustor capable of generating combustion gas by burning fuel in the compressed air compressed by the compressor, and a turbine capable of driving the combustion gas, a liquefaction equipment capable of liquefying gaseous air, and a liquefaction controller for controlling the liquefaction equipment. The compressor includes a compressor rotor capable of rotating about an axis, a compressor casing covering the outer periphery of the compressor rotor, a plurality of stator vanes provided on the inner periphery of the compressor casing, and an intake amount regulator capable of adjusting the intake amount, which is the flow rate of air flowing into the compressor casing, by opening and closing the compressor rotor. The liquefaction equipment includes an extraction line capable of extracting a portion of the compressed air from the compressor, a liquefaction system capable of liquefying the compressed air flowing through the extraction line, an extraction amount control valve capable of adjusting the flow rate of the compressed air flowing through the extraction line, a liquid air tank capable of storing liquid air, which is the compressed air liquefied in the liquefaction system, a return air line capable of directing the liquid air in the liquid air tank or return air, which is vaporized air formed by vaporizing the liquid air, to a flow path through which air or compressed air flows in the gas turbine, or to high-temperature components that come into contact with the combustion gas in components that constitute the gas turbine, and a return amount control valve capable of adjusting the flow rate of the return air flowing through the return air line. The liquefaction controller opens the extraction air amount control valve to guide the compressed air to the liquefaction system when the opening of the intake air amount regulator is at a first opening or a parameter correlated with the opening has a value corresponding to the first opening, and opens the return amount control valve to guide the return air to the gas turbine when the opening of the intake air amount regulator is at a second opening which is larger than the first opening or the parameter has a value corresponding to the second opening. The first opening is an opening when the amount of intake air flowing into the compressor casing is made smaller than the amount of intake air when the output of the gas turbine is at a rated output.

[0008] In this aspect, at the first degree of opening when the intake air volume is reduced below the intake air volume when the output of the gas turbine is at the rated output, a part of the compressed air from the compressor is bled to the liquefaction facility. This reduces the flow rate of compressed air flowing from the intermediate casing into the combustor. Therefore, at the first degree of opening, in this aspect, the flow rate of combustion gas generated in the combustor is reduced compared to when compressed air is not bled from the compressor, and the gas turbine output is reduced.

[0009] In this embodiment, at the second opening degree, which is larger than the first opening degree, the liquid air in the liquid air tank or the return air, which is the air obtained by vaporizing the liquid air, is guided to a flow path through which air or compressed air flows in the gas turbine, or to a high-temperature component that comes into contact with the combustion gas in a component that constitutes the gas turbine. For example, when the return air is guided to a flow path through which air or compressed air flows in the gas turbine at the second opening degree, the flow rate of the combustion gas generated in the combustor is greater than when the return air is not guided to this flow path, and the gas turbine output is increased. Also, when the return air is guided to a high-temperature component of the gas turbine at the second opening degree, the flow rate of the compressed air for cooling the high-temperature component is less than when the return air is not guided to the high-temperature component, and the flow rate of the air flowing into the combustor is greater, and the gas turbine output is increased.

[0010] Therefore, in this aspect, gas turbine output adjustment can be flexibly performed, and load fluctuations in the power system can be flexibly dealt with.

[0011] A method for operating a gas turbine plant as one aspect for achieving the above object is applied to the following gas turbine plant. This gas turbine plant includes a gas turbine having a compressor capable of compressing air, a combustor capable of generating combustion gas by burning fuel in the compressed air compressed by the compressor, and a turbine capable of being driven by the combustion gas. The compressor has a compressor rotor capable of rotating about an axis, a compressor casing covering the outer periphery of the compressor rotor, a plurality of stator vanes provided on the inner periphery of the compressor casing, and an intake air amount regulator capable of adjusting an intake air amount, which is the flow rate of air flowing into the compressor casing, by opening and closing the compressor rotor. The operating method includes an extraction step of extracting a part of the compressed air from the compressor, a liquefaction step of liquefying the compressed air extracted in the extraction step to generate liquid air, and a return step of guiding the liquid air or the vaporized air obtained by vaporizing the liquid air to a flow path through which air or compressed air flows in the gas turbine, or to a high-temperature component that comes into contact with the combustion gas among components constituting the gas turbine. The extraction step and the liquefaction step are performed when the opening degree of the intake air regulator is a first opening degree or a parameter having a correlation with the opening degree has a value corresponding to the first opening degree, and the return step is performed when the opening degree of the intake air regulator is a second opening degree larger than the first opening degree or the parameter has a value corresponding to the second opening degree. The first opening degree is an opening degree when the amount of intake air flowing into the compressor casing is made smaller than the amount of intake air when the output of the gas turbine is at a rated output.

[0012] By carrying out the operating method of this aspect, like the gas turbine plant of the above aspect, it is possible to flexibly adjust the gas turbine output and flexibly respond to load fluctuations in the power system.

[0013] A method for modifying a gas turbine plant as one aspect for achieving the above object is applied to the following gas turbine plant. This gas turbine plant includes a gas turbine having a compressor capable of compressing air, a combustor capable of generating combustion gas by burning fuel in the compressed air compressed by the compressor, and a turbine capable of being driven by the combustion gas. The compressor has a compressor rotor capable of rotating about an axis, a compressor casing covering the outer periphery of the compressor rotor, a plurality of stator vanes provided on the inner periphery of the compressor casing, and an intake air amount regulator capable of adjusting an intake air amount, which is the flow rate of air flowing into the compressor casing, by opening and closing the compressor rotor. The above-mentioned retrofitting method includes a step of adding a liquefaction facility capable of liquefying gaseous air and a liquefaction controller for controlling the liquefaction facility. The liquefaction facility added in the step includes a bleed line capable of bleeding a part of the compressed air from the compressor, a liquefaction system capable of liquefying the compressed air flowing through the bleed line, a liquid air tank capable of storing liquid air, which is the compressed air liquefied in the liquefaction system, a bleed amount control valve capable of adjusting the flow rate of the compressed air flowing through the bleed line, a return air line capable of guiding the liquid air in the liquid air tank or return air, which is vaporized air obtained by vaporizing the liquid air, to a flow path through which air or compressed air flows in the gas turbine, or to a high-temperature component that comes into contact with the combustion gas in a component constituting the gas turbine, and a return amount control valve capable of adjusting the flow rate of the return air flowing through the return air line. The liquefaction controller added in the step opens the extraction air amount control valve to guide the compressed air to the liquefaction system when the opening of the intake air amount regulator is at a first opening or a parameter correlated with the opening has a value corresponding to the first opening, and opens the return amount control valve to guide the return air to the gas turbine when the opening of the intake air amount regulator is at a second opening which is larger than the first opening or the parameter has a value corresponding to the second opening. The first opening is an opening when the amount of intake air flowing into the compressor casing is made smaller than the amount of intake air when the output of the gas turbine is at a rated output.

[0014] In a gas turbine plant retrofitted by the retrofit method of this aspect, like the gas turbine plant of the above aspect, gas turbine output adjustment can be flexibly performed and load fluctuations in the power system can be flexibly responded to. Effect of the Invention

[0015] In one aspect of the present disclosure, gas turbine output adjustment can be flexibly performed, and load fluctuations in the power system can be flexibly accommodated. [Brief description of the drawings]

[0016] [Figure 1] FIG. 1 is a system diagram of a gas turbine plant in a first embodiment according to the present disclosure. [Diagram 2] 4 is a graph showing a relationship between an IGV aperture and a gas turbine output in the first embodiment according to the present disclosure. [Diagram 3] 5 is a flowchart showing the operation of the liquefaction controller in the first embodiment of the present disclosure. [Figure 4] FIG. 4 is a system diagram of a gas turbine plant in a second embodiment according to the present disclosure. [Diagram 5] FIG. 4 is a cross-sectional view of a stator vane of a compressor in a second embodiment according to the present disclosure. [Figure 6] FIG. 11 is a system diagram of a gas turbine plant in a third embodiment according to the present disclosure. [Figure 7] FIG. 11 is a system diagram of a gas turbine plant in a fourth embodiment according to the present disclosure. [Figure 8] FIG. 2 is a system diagram of a modified liquefaction system according to the present disclosure. [Figure 9] 9 is a flowchart showing the operation of a liquefaction controller for a liquefaction facility including the liquefaction system of the modified example shown in FIG. 8. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0017] Hereinafter, various embodiments and various modified examples of a gas turbine plant according to the present disclosure will be described with reference to the drawings.

[0018] "First embodiment" Hereinafter, a first embodiment of a gas turbine plant according to the present disclosure will be described with reference to FIGS. 1 to 3. FIG.

[0019] As shown in FIG. 1 , the gas turbine plant of this embodiment includes a gas turbine 1, a GT generator 38 that generates electric power by driving the gas turbine 1, a GT power supply facility 39 that can supply electric power from the GT generator 38 to a power system PS, a turbine cooling device 30, a waste heat utilization facility 40 that utilizes the heat of the exhaust gas discharged from the gas turbine 1, a liquefaction facility 50 that can liquefy gaseous air, and a control device 100.

[0020] The gas turbine 1 includes a compressor 10 that compresses air A, a combustor 17 that burns fuel in the compressed air CA compressed by the compressor 10 to generate combustion gas, and a turbine 20 that is driven by the high-temperature, high-pressure combustion gas.

[0021] The compressor 10 includes a compressor rotor 11 that rotates about a rotor axis Ar, a compressor casing 14 that covers the compressor rotor 11, a plurality of stator vane rows 12t, and an intake air regulator (hereinafter referred to as an IGV (inlet guide vane)) 15. Here, the direction in which the rotor axis Ar extends is defined as an axial direction Da, and one of both sides of this axial direction Da is defined as an axial upstream side Dau, and the other side is defined as an axial downstream side Dad.

[0022] The compressor rotor 11 has a compressor rotor shaft 11a extending in an axial direction Da about the rotor axis Ar, and a plurality of rotor blade rows 11t fixed to the compressor rotor shaft 11a. The plurality of rotor blade rows 11t are arranged in the axial direction Da. Each of the plurality of rotor blade rows 11t has a plurality of rotor blades 11b arranged in a circumferential direction with respect to the rotor axis Ar. Each of the plurality of stator blade rows 12t is disposed on the axial downstream side Dad of any one of the plurality of rotor blade rows 11t. Each of the plurality of stator blade rows 12t has a plurality of stator vanes 12v arranged in a circumferential direction with respect to the rotor axis Ar. The plurality of stator vanes 12v are fixed to an inner peripheral portion of the compressor casing 14.

[0023] The IGV 15 has a plurality of guide vanes 15v arranged on the axial upstream side Dau of the plurality of rotor blade rows 11t inside the compressor casing 14, and a driver 15d that opens and closes the plurality of guide vanes 15v. The IGV 15 can adjust the intake air amount, which is the flow rate of air flowing into the compressor casing 14.

[0024] The turbine 20 is disposed on the axial downstream side Dad of the compressor 10. The turbine 20 has a turbine rotor 21 that rotates about a rotor axis Ar by combustion gas from the combustor 17, a turbine casing 24 that covers the turbine rotor 21, and a plurality of stator blade rows 22t.

[0025] The turbine rotor 21 has a turbine rotor shaft 21a extending in an axial direction Da centered on the rotor axis Ar, and a plurality of rotor blade rows 21t fixed to the turbine rotor shaft 21a. The plurality of rotor blade rows 21t are arranged in the axial direction Da. Each of the plurality of rotor blade rows 21t has a plurality of rotor blades 21b arranged in a circumferential direction with respect to the rotor axis Ar. Each of the plurality of stator blade rows 22t is disposed on the axial upstream side Dau of any one of the plurality of rotor blade rows 21t. Each of the plurality of stator blade rows 22t has a plurality of stator vanes 22v arranged in a circumferential direction with respect to the rotor axis Ar. The plurality of stator vanes 22v are fixed to an inner peripheral portion of the turbine casing 24.

[0026] The turbine rotor 21 and the compressor rotor 11 are connected to each other so as to be integrally rotatable about the same rotor axis Ar to form a gas turbine rotor 2. To this gas turbine rotor 2, a rotor of a GT generator 38 is connected.

[0027] The gas turbine 1 further includes an intermediate casing 4. The intermediate casing 4 is disposed between the compressor casing 14 and the turbine casing 24 in the direction in which the rotor axis Ar extends, and connects the compressor casing 14 and the turbine casing 24. The gas turbine casing 3 includes the compressor casing 14, an intermediate casing 4, and the turbine casing 24. Compressed air CA discharged from the compressor 10 flows into the intermediate casing 4. The combustor 17 is fixed to the intermediate casing 4. A fuel line 5 is connected to the combustor 17. The fuel line 5 is provided with a fuel control valve 6 that adjusts the flow rate of fuel flowing through the fuel line 5. The combustor 17 includes a combustion liner (or transition piece) 17c and a fuel nozzle 17n that injects fuel into the combustion liner 17c.

[0028] The GT power supply facility 39 includes a GT power line 39a that electrically connects the GT generator 38 and the power system PS, and a GT circuit breaker 39b and a GT transformer 39t that are provided in the GT power line 39a. A GT power meter 39m that measures the power flowing through the GT power line 39a is provided on the GT power line 39a.

[0029] The turbine cooling device 30 includes a cooling bleed air line 31, a cooler 32, and a cooling air line 33. The cooling bleed air line 31 is capable of bleeding the compressed air CA from the compressor 10. For this purpose, one end of the cooling bleed air line 31 is connected to the intermediate casing 4 that forms a flow path through which the compressed air CA from the compressor 10 flows. The cooling bleed air line 31 is provided with a cooling bleed air amount control valve 31v that adjusts the flow rate of the compressed air CA flowing through the bleed air line 51. The cooler 32 is connected to the other end of the cooling bleed air line 31, and cools the compressed air CA that has flowed through the bleed air line 51. The cooling air line 33 is connected to the cooler 32, and the cooling air, which is the compressed air CA cooled by the cooler 32, flows through the cooling air line 33. The cooling air line 33 includes a main cooling air line 33m, a combustor cooling air line 33c, a rotor blade cooling air line 33b, and a stationary blade cooling air line 33v. The combustor cooling air line 33c, the moving blade cooling air line 33b, and the stationary blade cooling air line 33v are all lines branched off from the main cooling air line 33m.

[0030] Among the components constituting the gas turbine 1, the combustion liner 17c of the combustor 17 and the multiple rotor blades 21b and the multiple stator blades 22v of the turbine 20 are all high-temperature components that come into contact with the combustion gas. These high-temperature components are formed with a cooling air passage 23 that passes through the high-temperature components and opens on the surface of the high-temperature components that comes into contact with the combustion gas. The turbine rotor shaft 21a is formed with a cooling air passage 21ap that passes through the turbine rotor shaft 21a and communicates with the cooling air passage 23 of any one of the multiple rotor blades 21b.

[0031] The combustor cooling air line 33c is connected to the cooling air passage of the combustion liner 17c, which is a type of high-temperature component. The rotor blade cooling air line 33b is connected to the cooling air passage 23 of the rotor blade 21b, which is a type of high-temperature component, via the cooling air passage 21ap of the turbine rotor shaft 21a. The stator blade cooling air line 33v is connected to the cooling air passage 23 of any one of the multiple stator blades 22v.

[0032] In this embodiment, among the combustor cooling air line 33c, the moving blade cooling air line 33b, and the stationary blade cooling air line 33v, the cooling air control valve 34 is provided in the combustor cooling air line 33c and the stationary blade cooling air line 33v. However, it is sufficient that the cooling air control valve 34 is provided in any two of the combustor cooling air line 33c, the moving blade cooling air line 33b, and the stationary blade cooling air line 33v. The turbine cooling device 30 of this embodiment supplies cooling air to all of the combustion liner 17c of the combustor 17 and the multiple moving blades 21b and the multiple stationary blades 22v of the turbine 20, and cools all of these high-temperature components. However, the turbine cooling device 30 may supply cooling air to only one of the high-temperature components among the combustion liner 17c of the combustor 17 and the multiple moving blades 21b and the multiple stationary blades 22v of the turbine 20, and cool only this one high-temperature component.

[0033] The waste heat utilization equipment 40 includes a waste heat recovery boiler 41, a chimney 42, a steam turbine 43 driven by steam from the waste heat recovery boiler 41, a main steam line 44 capable of directing steam generated in the waste heat recovery boiler 41 to the steam turbine 43, a condenser 45 that converts steam exhausted from the steam turbine 43 back into water, a water supply line 46 that can direct the water in the condenser 45 to the waste heat recovery boiler 41, a water supply pump 47 provided in the water supply line 46, a ST generator 48 that generates electricity by driving the steam turbine 43, and a ST power supply equipment 49 that can supply electricity from the ST generator 48 to the power system PS.

[0034] The heat recovery boiler 41 can evaporate water to generate steam by utilizing the heat of the exhaust gas, which is the combustion gas discharged from the turbine 20. The heat recovery boiler 41 has a duct 41d connected to the turbine casing 24 and a heat transfer tube 41t disposed in the duct 41d. Exhaust gas from the turbine 20 flows in the duct 41d. Liquid water or gaseous water flows in the heat transfer tube 41t. One end of the heat transfer tube 41t forms a water inlet and is connected to a water supply line 46. The other end of the heat transfer tube 41t forms a steam outlet and is connected to a main steam line 44. The chimney 42 is connected to the duct 41d of the heat recovery boiler 41.

[0035] The ST power supply facility 49 includes an ST power line 49a that electrically connects the ST generator 48 and the power system PS, and an ST circuit breaker 49b and an ST transformer 49t provided in the ST power line 49a. An ST power meter 49m that measures the power flowing through the ST power line 49a is provided on the ST power line 49a.

[0036] The liquefaction facility 50 includes an extraction line 51 , an extraction amount control valve 52 , a liquefaction system 60 , a liquid air tank 53 , a heating system 80 , a return air line 54 , a liquid air pump 56 , and a return amount control valve 57 .

[0037] The bleed line 51 is capable of bleeding out a portion of the compressed air CA from the compressor 10. For this reason, one end of this bleed line 51 is connected to the intermediate casing 4 which forms a flow path through which the compressed air CA from the compressor 10 flows. A bleed amount control valve 52 is provided in this bleed line 51. This bleed amount control valve 52 is capable of adjusting the flow rate of the compressed air CA flowing through the bleed line 51.

[0038] The liquefaction system 60 has a primary cooler (second cooling heat exchanger) 61, a secondary cooler 62, a cooling device 63, a gas-liquid separation tank 77, a liquid air supply line 78, and a liquid air supply control valve 79.

[0039] The cooling device 63 is capable of cooling the compressed air CA from the extraction line 51. The cooling device 63 has a boost compressor 64, an expansion turbine 65, a tertiary cooler 66, a quaternary cooler (first cooling heat exchanger) 67, a high-compressed air main line 68m, a high-compressed air branch line 68b, a high-compressed air control valve 68v, a low-temperature low-pressure air main line 69m, a low-temperature low-pressure air branch line 69b, a gas-liquid mixing line 74, and an expansion valve 75.

[0040] The other end of the above-mentioned extraction line 51 is connected to the intake port of the boost compressor 64. The boost compressor 64 can further compress the compressed air CA from the extraction line 51 to generate high-compressed air HCA. The discharge port of the boost compressor 64 and the high-compressed air inlet of the quaternary cooler 67 are connected by a high-compressed air main line 68m. In the high-compressed air main line 68m, a tertiary cooler 66 capable of heat-exchanging the high-compressed air HCA with a cooling medium such as seawater, river water, or groundwater is provided. The high-compressed air branch line 68b is a line branched from a position between the tertiary cooler 66 and the quaternary cooler 67 in the high-compressed air main line 68m. The high-compressed air branch line 68b is connected to the intake port of the expansion turbine 65. The high-compressed air branch line 68b is provided with a high-compressed air control valve 68v that adjusts the flow rate of the high-compressed air HCA flowing through the high-compressed air branch line 68b. The expansion turbine 65 can generate low-temperature, low-pressure air LLA by adiabatically expanding the high-compressed air HCA from the high-compressed air branch line 68b. One end of a low-temperature, low-pressure air main line 69m is connected to the exhaust port of the expansion turbine 65. The other end of the low-temperature, low-pressure air main line 69m is connected to the low-temperature, low-pressure air inlet of the quaternary cooler 67. Therefore, the quaternary cooler (first cooling heat exchanger) 67 can cool the high-compressed air HCA by exchanging heat between the high-compressed air HCA that has passed through the tertiary cooler 66 and the low-temperature, low-pressure air LLA from the expansion turbine 65. A part of the high-compressed air HCA cooled by the quaternary cooler (first cooling heat exchanger) 67 becomes liquid air LA, and the remainder remains as cooled high-compressed air HCA. Meanwhile, the low-temperature, low-pressure air LLA heated by heat exchange with the high-compressed air HCA is released from the quaternary cooler 67 to the atmosphere. The low-temperature, low-pressure air branch line 69b is a line branched off from the low-temperature, low-pressure air main line 69m. This low-temperature, low-pressure air branch line 69b is connected to a gas-liquid separation tank 77. The gas-liquid mixture outlet of the quaternary cooler 67 and the gas-liquid separation tank 77 are connected by a gas-liquid mixture line 74. The cooled highly compressed air HCA and liquid air LA from the quaternary cooler (first cooling heat exchanger) 67 flow through this gas-liquid mixture line 74. An expansion valve 75 is provided in this gas-liquid mixture line 74.The expansion valve 75 adiabatically expands the fluid flowing through the gas-liquid mixing line 74, promoting the liquefaction of the fluid.

[0041] A primary cooler (second cooling heat exchanger) 61 is provided in the extraction line 51 at a position between the extraction amount control valve 52 and the boost compressor 64. This primary cooler (second cooling heat exchanger) 61 exchanges heat between the compressed air CA flowing through the extraction line 51 and the heat storage material HG, and is capable of heating the heat storage material HG while cooling the compressed air CA. A secondary cooler 62 is provided in the extraction line 51 at a position between the primary cooler 61 and the boost compressor 64. This secondary cooler 62 is capable of cooling the compressed air CA by exchanging heat between the compressed air CA from the primary cooler 61 and a cooling medium such as seawater, river water, or groundwater.

[0042] The highly compressed air HCA and liquid air LA from the quaternary cooler (first cooling heat exchanger) 67 can flow into the gas-liquid separation tank 77 via the gas-liquid mixing line 74. The liquid air LA and the gaseous air are separated inside this gas-liquid separation tank 77. The gaseous air is released into the atmosphere via the low-temperature low-pressure air branch line 69b and the quaternary cooler 67.

[0043] A liquid air supply line 78 connects the gas-liquid separation tank 77 and the liquid air tank 53 . The liquid air supply adjustment valve 79 is capable of adjusting the flow rate of the liquid air LA flowing through the liquid air supply line 78 .

[0044] The heating system 80 includes a first heating device 81 capable of heating the liquid air LA from the liquid air tank 53 to generate vaporized air VA from the liquid air LA, a second heating device 88 capable of heating the vaporized air VA from the first heating device 81, and a third heating device 95 capable of heating the vaporized air VA from the second heating device 88. Note that, hereinafter, the liquid air LA and the vaporized air VA will be collectively referred to as return air RA.

[0045] The first heating device 81 has a gas-liquid tank 82 capable of storing liquid air LA and vaporized air VA produced by vaporizing the liquid air LA, a primary heater (first heating heat exchanger) 67, a heating liquid air line 83, a heating liquid air pump 84, a heating liquid air control valve 85, and a vaporized air return line 86.

[0046] The heating liquid air line 83 connects the liquid air outlet of the gas-liquid tank 82 and the liquid air inlet of the primary heater 67. A heating liquid air pump 84 and a heating liquid air adjustment valve 85 are provided in this heating liquid air line 83. The vaporized air return line 86 connects the vaporized air outlet of the primary heater 67 and the vaporized air inlet of the gas-liquid tank 82.

[0047] The primary heater (first heating heat exchanger) 67 is a heat exchanger that exchanges heat between the compressed air CA and the liquid air LA, and is also the above-mentioned quaternary cooler (first cooling heat exchanger) 67. Therefore, this primary heater (first heating heat exchanger) 67 can exchange heat between the liquid air LA from the gas-liquid tank 82 and the low-temperature low-pressure air LLA from the low-temperature low-pressure air main line 69m, and the high-compressed air HCA from the high-compressed air main line 68m. The primary heater (first heating heat exchanger) 67, the heating liquid air line 83, the heating liquid air pump 84, the heating liquid air control valve 85, and the vaporized air return line 86 of the first heating device 81 also constitute a part of the cooling device 63 in the liquefaction system 60.

[0048] The second heating device 88 has a heat storage tank 89 capable of storing a fluid heat storage material HG, a secondary heater (second heating heat exchanger) 91, a heat storage material supply line 92, a heat storage material supplier 92p, a high-temperature heat storage material line 93, a heat storage material control valve 93v, and a low-temperature heat storage material line 94.

[0049] The heat storage material supply line 92 connects the heat storage material outlet of the heat storage tank 89 and the heat storage material inlet of the secondary heater 91. This heat storage material supply device 92p is provided on the heat storage material supply line 92. The heat storage material supply device 92p is a blower when the heat storage material HG flowing through the heat storage material supply line 92 is a gas, and is a pump when the heat storage material HG flowing through the heat storage material supply line 92 is a liquid.

[0050] The secondary heater (second heating heat exchanger) 91 exchanges heat between the heat storage material HG from the heat storage tank 89 and the vaporized air VA, and is capable of heating the vaporized air VA while cooling the heat storage material HG.

[0051] The high-temperature heat storage material line 93 connects the heat storage material outlet of the secondary heater 91 and the heat storage material inlet of the primary cooler (second cooling heat exchanger) 61. Therefore, the primary cooler (second cooling heat exchanger) 61 exchanges heat between the heat storage material HG cooled by the secondary heater (second heating heat exchanger) 91 and the compressed air CA, and can cool the compressed air CA while heating the heat storage material HG. The high-temperature heat storage material line 93 is provided with a heat storage material control valve 93v that can adjust the flow rate of the heat storage material HG flowing through the high-temperature heat storage material line 93 and the heat storage material supply line 92. The low-temperature heat storage material line 94 connects the heat storage material outlet of the primary cooler (second cooling heat exchanger) 61 and the heat storage material inlet of the heat storage tank 89. Therefore, the heat storage material HG heated by the primary cooler (second cooling heat exchanger) 61 flows into the heat storage tank 89.

[0052] The third heating device 95 has a tertiary heater (third heating heat exchanger) 96, a branch steam line 97, and a branch steam control valve 97v.

[0053] The branch steam line 97 is a line branched off from the main steam line 44 of the exhaust heat utilization equipment 40. This branch steam line 97 is connected to a steam inlet of a tertiary heater 96. A branch steam control valve 97v is provided in the branch steam line 97. The tertiary heater (third heating heat exchanger) 96 exchanges heat between the vaporized air VA heated by the second heating device 88 and steam, thereby being capable of heating the vaporized air VA and cooling the steam. The steam cooled by heat exchange with the vaporized air VA in the tertiary heater 96 is returned to the condenser 45, for example.

[0054] The return air line 54 has a liquid air line 55 and a vaporized air line 58. The liquid air line 55 connects the liquid air outlet of the liquid air tank 53 and the liquid air inlet of the gas-liquid tank 82. The liquid air line 55 is provided with a liquid air pump 56 and a return amount control valve 57. The return amount control valve 57 can adjust the flow rate of the return air RA flowing through the return air line 54. The vaporized air line 58 connects the vaporized air outlet of the gas-liquid tank 82 and the intermediate casing 4 that forms a flow path through which the compressed air CA from the compressor 10 flows. The vaporized air line 58 is provided with a secondary heater (second heating heat exchanger) 91. A tertiary heater (third heating heat exchanger) 96 is provided in the vaporized air line 58 between the secondary heater (second heating heat exchanger) 91 and the intermediate casing 4.

[0055] The control device 100 has a fuel controller 101, an IGV controller 102, and a liquefaction controller 103.

[0056] The fuel controller 101 receives as input the power value measured by the GT power meter 39m and the power value measured by the ST power meter 49m. The power value measured by the GT power meter 39m is the actual output value of the gas turbine 1. The power value measured by the ST power meter 49m is the actual output value of the steam turbine 43. Therefore, the power value obtained by adding the power value measured by the GT power meter 39m and the power value measured by the ST power meter 49m is the actual output value of the gas turbine plant. A load command LC is also input from the outside to the fuel controller 101. This load command LC indicates a required output value of the gas turbine plant. The fuel controller 101 calculates the fuel flow rate to be supplied to the combustor 17 according to the power value obtained by adding the power value measured by the GT power meter 39m and the power value measured by the ST power meter 49m, that is, the deviation between the actual output value of the gas turbine plant and the required output value of the gas turbine plant indicated by the load command LC. The fuel controller 101 further obtains the valve opening of the fuel regulating valve 6 according to this fuel flow rate, and sends this valve opening to the fuel regulating valve 6 .

[0057] As shown in FIG. 2, the IGV controller 102 has a function indicating the relationship between the fuel flow rate determined by the fuel controller 101 or the gas turbine output corresponding to this fuel flow rate, and the IGV opening θ. This function is a function in which the IGV opening θ increases as the fuel flow rate determined by the fuel controller 101 or the gas turbine output corresponding to this fuel flow rate increases. Note that the IGV opening θ is the opening of the multiple guide vanes 15v. When the IGV opening θ, that is, the opening of the multiple guide vanes 15v, increases, the amount of intake air of the compressor 10 increases. The IGV controller 102 uses this function to determine the IGV opening θ corresponding to the fuel flow rate determined by the fuel controller 101 or the gas turbine output. Then, the IGV controller 102 sends this IGV opening θ to the driver 15d of the IGV 15.

[0058] The liquefaction controller 103 controls the operation of the liquefaction equipment 50 in response to the IGV opening θ or the load command LC. The operation of the liquefaction controller 103 and the operation of the liquefaction equipment 50 based on this operation will be described in detail later. Note that, as described above, the load command LC is a type of parameter that has a correlation with the IGV opening θ.

[0059] The control device 100 described above is a computer. Therefore, in terms of hardware, the control device 100 has a CPU (Central Processing Unit) that performs various calculations, a main storage device such as a memory that serves as a work area for the CPU, an auxiliary storage device such as a hard disk drive device, input devices such as a keyboard and a mouse, and a display device. Each functional unit in the control device 100, such as the fuel controller 101, the IGV controller 102, and the liquefaction controller 103, functions by, for example, the CPU executing a control program stored in the auxiliary storage device.

[0060] Next, the operation of the gas turbine plant described above will be described.

[0061] The compressor 10 of the gas turbine 1 compresses air A to generate compressed air CA. The compressed air CA from the compressor 10 passes through the intermediate casing 4 and flows into the combustor 17. Fuel also flows into the combustor 17. In the combustion tube 17c of the combustor 17, the fuel is combusted in the compressed air CA to generate high-temperature, high-pressure combustion gas. This combustion gas is sent from the combustor 17 to a combustion gas flow path in the turbine 20, and rotates the turbine rotor 21. The rotation of the turbine rotor 21 causes the GT generator 38 connected to the gas turbine rotor 2 to generate electricity.

[0062] As described above, the combustion tube 17c of the combustor 17 and the multiple rotor blades 21b and multiple stator vanes 22v of the turbine 20 are all high-temperature components that come into contact with the combustion gas. In order to increase the durability of these high-temperature components, in this embodiment, cooling air is supplied to these high-temperature components to cool them. Specifically, in this embodiment, compressed air CA is extracted from the intermediate casing 4 through which the compressed air CA from the compressor 10 flows, and this compressed air CA is cooled by the cooler 32 to become cooled air. This cooled air is then sent to each high-temperature component.

[0063] The combustion gas that rotates the turbine rotor 21 is exhausted from the turbine 20 as exhaust gas and is then discharged into the atmosphere from a chimney 42 via a duct 41d of the heat recovery boiler 41. In the duct 41d of the heat recovery boiler 41, while the exhaust gas passes through, heat is exchanged between the exhaust gas and water or steam in a heat transfer tube 41t arranged in the duct 41d, generating high-temperature, high-pressure steam.

[0064] This steam is sent to the steam turbine 43 via the main steam line 44. The steam turbine 43 is driven by this steam. The steam turbine 43 drives an ST generator 48 connected to the steam turbine 43 to generate electricity. The steam exhausted from the steam turbine 43 is returned to water by a condenser 45. The water in the condenser 45 is returned to the inside of the heat transfer tubes 41t of the heat recovery boiler 41 via a water feed line 46.

[0065] As described above, the fuel controller 101 of the control device 100 determines the fuel flow rate to be supplied to the combustor 17 according to the deviation between the required output value of the gas turbine plant indicated by the load command LC and the actual output value of the gas turbine plant, etc. For this reason, when the required output value of the gas turbine plant indicated by the load command LC increases, the fuel flow rate to be supplied to the combustor 17 increases, and when the required output value of the gas turbine plant indicated by the load command LC decreases, the fuel flow rate to be supplied to the combustor 17 decreases. In addition, the IGV controller 102 determines the IGV opening θ according to the fuel flow rate or the gas turbine output, using the function shown in Fig. 2. For this reason, when the fuel flow rate increases and the gas turbine output increases, the IGV opening θ increases, and when the fuel flow rate decreases and the gas turbine output decreases, the IGV opening θ decreases.

[0066] As shown in Fig. 2, the IGV opening θ has a minimum opening min and a maximum opening max. When the gas turbine output is at the rated output, the IGV opening θ is at the maximum opening max. Also, when the gas turbine output is at the minimum output, the IGV opening θ is at the minimum opening min. Here, the minimum opening min is defined as the first opening θ1, and the maximum opening max is defined as the second opening θ2. Therefore, the first opening θ1 is the opening when the amount of intake air flowing into the compressor casing 14 is made less than the amount of intake air when the gas turbine output is at the rated output.

[0067] 3, the liquefaction controller 103 monitors whether the IGV opening θ is the first opening θ1 or the second opening θ2 (opening monitoring step S1). The liquefaction controller 103 determines whether the IGV opening θ is the first opening θ1 or the second opening θ2 from any one of the IGV opening θ indicated by the control signal sent from the IGV controller 102 to the IGV 15, the fuel flow rate determined by the fuel controller 101, and the power value from the GT power meter 39m.

[0068] When the liquefaction controller 103 determines in the opening monitoring step S1 that the IGV opening θ is the first opening θ1 (minimum opening min), it outputs an open command to the extraction air amount control valve 52. As a result, the extraction air amount control valve 52 opens, and the extraction step S2 is performed. In this extraction step S2, the compressed air CA in the intermediate casing 4 flows into the liquefaction system 60 via the extraction line 51.

[0069] When the liquefaction controller 103 determines that the IGV opening θ is the first opening θ1 (minimum opening min), it drives the liquefaction system 60. As a result, the liquefaction process S3 and the vaporization process S4 are executed. In the liquefaction process S3, first, in the primary cooler (second cooling heat exchanger) 61, heat is exchanged between the compressed air CA flowing through the extraction line 51 and the heat storage material HG, and the heat storage material HG is heated while the compressed air CA is cooled. The heated heat storage material HG flows into the heat storage tank 89. Meanwhile, in the secondary cooler 62, the cooled compressed air CA is heat exchanged with a cooling medium such as seawater, river water, or groundwater, and the compressed air CA is further cooled.

[0070] The compressed air CA cooled by the secondary cooler 62 is compressed by the boost compressor 64 to become highly compressed air HCA. This highly compressed air HCA is cooled by heat exchange with a cooling medium such as seawater, river water, or groundwater in the tertiary cooler 66. A portion of the highly compressed air HCA cooled in the tertiary cooler 66 flows into the expansion turbine 65 via the highly compressed air branch line 68b. This highly compressed air HCA is adiabatically expanded in the expansion turbine 65 to become low-temperature, low-pressure air LLA. The low-temperature, low-pressure air LLA flows into the quaternary cooler 67 via the low-temperature, low-pressure air main line 69m. In addition, in this liquefaction step S3, the heating liquid air pump 84 of the first heating device 81 is driven, and the heating liquid air control valve 85 of the first heating device 81 is opened. Therefore, the liquid air LA in the gas-liquid tank 82 of the first heating device 81 flows into the quaternary cooler 67. As a result, in the quaternary cooler (first cooling heat exchanger) 67, the liquid air LA from the gas-liquid tank 82 and the low-temperature, low-pressure air LLA from the low-temperature, low-pressure air main line 69m are heat exchanged with another part of the high-compressed air HCA, and the other part of the high-compressed air HCA is cooled, and at least a part of it becomes liquid air LA. This liquid air LA flows into the gas-liquid mixing line 74 together with the high-compressed air HCA that was not liquefied in the quaternary cooler 67. The fluid that has flowed into the gas-liquid mixing line 74 is adiabatically expanded by the expansion valve 75 provided in the gas-liquid mixing line 74, promoting liquefaction. The liquid air LA from the gas-liquid tank 82 is heated and vaporized by heat exchange with the highly compressed air HCA in the quaternary cooler (primary heater, first heating heat exchanger) 67, and returns to the gas-liquid tank 82. Therefore, in this liquefaction step S3, the liquid air LA in the gas-liquid tank 82 gradually decreases, and the vaporized air VA in the gas-liquid tank 82 gradually increases. That is, in this liquefaction step S3, a vaporization step S4 is also performed in which the liquid air LA is vaporized to generate the vaporized air VA. In addition, the low-temperature low-pressure air LLA from the expansion turbine 65 is heated by heat exchange with the highly compressed air HCA in the quaternary cooler 67, and then released into the atmosphere.

[0071] The fluid whose liquefaction has been promoted by the expansion valve 75 flows into the gas-liquid separation tank 77 and is separated into gaseous air and liquid air LA. The liquid air LA in the gas-liquid separation tank 77 flows into the liquid air tank 53 via the liquid air supply line 78.

[0072] When the IGV opening θ is the first opening θ1 (minimum opening min), the above-mentioned extraction process S2, liquefaction process S3, and vaporization process S4 are continuously performed.

[0073] As described above, when the IGV opening θ is the first opening θ1 (minimum opening min), the compressed air CA inside the intermediate casing 4 is extracted, and the flow rate of the compressed air CA flowing from inside the intermediate casing 4 into the combustor 17 decreases. As a result, the flow rate of the combustion gas generated in the combustor 17 decreases compared to when the compressed air CA inside the intermediate casing 4 is not extracted, and the gas turbine output decreases.

[0074] When the liquefaction controller 103 determines in the opening monitoring process S1 that the IGV opening θ is not the first opening θ1 (minimum opening min), it closes the extraction amount control valve 52 to stop the extraction process S2 and also stops the liquefaction system 60 to stop the liquefaction process S3.

[0075] When the liquefaction controller 103 determines in the opening monitoring step S1 that the IGV opening θ is the second opening θ2 (maximum opening max), it outputs an open command to the return amount adjustment valve 57 and outputs a drive command to the liquid air pump 56 and the heating system 80. As a result, the return amount adjustment valve 57 opens, the liquid air pump 56 and the heating system 80 are driven, and the return step S5 and the heating step S6 are performed.

[0076] In the return step S5, the liquid air LA in the liquid air tank 53 flows into the gas-liquid tank 82 through the liquid air line 55 in the return air line 54. As a result, the amount of liquid air LA in the gas-liquid tank 82 increases, and the vaporized air VA in the gas-liquid tank 82 is pushed out by this liquid air LA. This vaporized air VA flows into the intermediate casing 4 through the secondary heater 91, the tertiary heater 96, and the vaporized air line 58 in the return air line 54. In the heating step S6, the vaporized air VA is heated by the secondary heater 91 and the tertiary heater 96 provided in the vaporized air line 58. The vaporized air VA from the gas-liquid tank 82 and the heat storage material HG from the heat storage tank 89 heated in the liquefaction step S3 flow into the secondary heater 91. As a result, in the secondary heater (second heating heat exchanger) 91, the heated heat storage material HG and the vaporized air VA exchange heat, and the heat storage material HG is cooled while the vaporized air VA is heated. The cooled heat storage material HG passes through the primary cooler (second cooling heat exchanger) 61 and then returns to the heat storage tank 89. Meanwhile, the vaporized air VA heated by heat exchange with the heat storage material HG flows into the tertiary heater 96 via the vaporized air line 58. Steam from the exhaust heat recovery boiler 41 also flows into the tertiary heater 96. As a result, in the tertiary heater (third heating heat exchanger) 96, heat exchange occurs between the heated vaporized air VA and steam, and the heated vaporized air VA is further heated while the steam is cooled. The cooled steam is returned to, for example, the condenser 45. Meanwhile, the further heated vaporized air VA flows into the intermediate casing 4 via the vaporized air line 58 as described above.

[0077] When the IGV opening θ is the second opening θ2 (maximum opening max), the return process S5 and the heating process S6 described above are continuously executed in parallel.

[0078] As described above, when the IGV opening θ is the second opening θ2 (maximum opening max), heated vaporized air VA flows into the intermediate casing 4, so that the flow rate of compressed air CA (including heated vaporized air VA) flowing from the intermediate casing 4 into the combustor 17 increases. As a result, the flow rate of the combustion gas generated in the combustor 17 becomes larger than in the case where the vaporized air VA in the intermediate casing 4 is not allowed to flow in, and the gas turbine output increases.

[0079] As described above, in this embodiment, when the IGV opening θ is the first opening θ1 (minimum opening min), the compressed air CA in the intermediate casing 4 is extracted to reduce the gas turbine output, and when the IGV opening θ is the second opening θ2 (maximum opening max), the high-temperature vaporized air VA in the intermediate casing 4 is allowed to flow in to increase the gas turbine output. Therefore, in this embodiment, gas turbine output adjustment can be flexibly performed, and load fluctuations in the power system can be flexibly accommodated.

[0080] In this embodiment, in the liquefaction step S3, the compressed air CA is cooled using low-temperature thermal energy obtained in the evaporation step S4 and the heating step S6. Also, in this embodiment, in the evaporation step S4 and the heating step S6, the liquid air LA and the vaporized air VA are heated using high-temperature thermal energy obtained in the liquefaction step S3. Therefore, in this embodiment, the amount of thermal energy supplied from outside the liquefaction equipment 50 can be reduced.

[0081] In the opening monitoring step S1 in the above embodiment, the liquefaction controller 103 monitors the IGV opening θ. As described above, the change in the IGV opening θ has a correlation with the change in the load command LC. For this reason, in the opening monitoring step S1, the load command LC from the outside may be monitored instead of the IGV opening θ. As described above, when the gas turbine output is the rated output, the IGV opening θ becomes the maximum opening max (second opening θ2), and when the gas turbine output is the minimum output, the IGV opening θ becomes the minimum opening min (first opening θ1). Therefore, when the load command LC is monitored in the opening monitoring step S1, it is sufficient to monitor whether the output value indicated by the load command LC is the output value (second output value) at which the gas turbine output should be the rated output, or the output value indicated by the load command LC is the output value (first output value) at which the gas turbine output should be the minimum output. Note that the first output value corresponds to the first opening θ1, and the second output corresponds to the second opening θ2.

[0082] Second Embodiment Next, a second embodiment of a gas turbine plant according to the present disclosure will be described with reference to FIGS.

[0083] 4, the gas turbine plant of this embodiment includes, like the gas turbine plant of the first embodiment, a gas turbine 1, a GT generator 38, a GT power supply system 39, a turbine cooling system 30, a waste heat utilization system 40, a liquefaction system 50a, and a control device 100. However, the liquefaction system 50a of this embodiment is different from the liquefaction system 50 of the first embodiment.

[0084] The liquefaction equipment 50a of this embodiment includes an extraction line 51, an extraction amount control valve 52, a liquefaction system 60a, a liquid air tank 53, a heating system 80a, a return air line 54a, a liquid air pump 56, and a return amount control valve 57, similar to the liquefaction equipment 50 of the first embodiment. However, in this embodiment, the return destination of the return air RA through the return air line 54a is different from that of the first embodiment. Therefore, the heating system 80a of this embodiment is different from the heating system 80 of the first embodiment. Furthermore, the liquefaction system 60a of this embodiment is different from the liquefaction system 60 of the first embodiment.

[0085] The return air line 54a of this embodiment has a liquid air line 55 and a vaporized air line 58a, similar to the return air line 54 of the first embodiment. The vaporized air line 58a is connected to the compressor casing 14, which is different from the vaporized air line 58 of the first embodiment. That is, in this embodiment, the return air RA is returned to the air flow path through which the air flows in the compressor 10. Specifically, the vaporized air line 58a of this embodiment is connected to a position Dau on the axial upstream side of the position where the multiple guide vanes 15v of the IGV 15 are arranged in the compressor casing 14. That is, in this embodiment, the return air RA is returned to the flow path portion through which the air flows before the intake amount is adjusted by the IGV 15 in the air flow path of the compressor 10. The temperature of the air flowing through the air flow path of the compressor 10 is lower than the temperature of the compressed air CA flowing into the combustor 17. Therefore, the temperature of the return air RA in this embodiment may be lower than the temperature of the return air RA in the first embodiment. Therefore, the heating system 80a of this embodiment differs from the heating system 80 of the first embodiment, as described above.

[0086] The heating system 80a of the present embodiment includes a first heating device 81 capable of heating the liquid air LA from the liquid air tank 53 to generate vaporized air VA. However, the heating system 80a of the present embodiment does not include the second heating device 88 and the third heating device 95 in the heating system 80 of the first embodiment. Therefore, the vaporized air line 58a of the present embodiment is not provided with the secondary heater 91 and the tertiary heater 96 in the first embodiment.

[0087] The heating system 80a of this embodiment does not include the second heating device 88 and the third heating device 95 of the first embodiment, and thus the liquefaction system 60a of this embodiment is different from the liquefaction system 60 of the first embodiment. The liquefaction system 60a of this embodiment has a primary cooler 62a similar to the secondary cooler 62 of the first embodiment, a cooling device 63, a gas-liquid separation tank 77, a liquid air supply line 78, and a liquid air supply control valve 79. The cooling device 63 has a boost compressor 64, an expansion turbine 65, a tertiary cooler 66, a quaternary cooler (first cooling heat exchanger) 67, a high-compressed air main line 68m, a high-pressure air branch line, a low-temperature low-pressure air main line 69m, a low-temperature low-pressure air branch line 69b, a gas-liquid mixing line 74, a high-compressed air control valve 68v, and an expansion valve 75, similar to the cooling device 63 of the first embodiment. The primary heater (first heating heat exchanger) 67, heating liquid air line 83, vaporized air return line 86, heating liquid air pump 84, and heating liquid air control valve 85 of the first heating device 81 in this embodiment also constitute part of the cooling device 63, as in the first embodiment.

[0088] The liquefaction controller 103 of the control device 100 monitors whether the IGV opening degree θ is the first opening degree θ1 or the second opening degree θ2, as in the first embodiment.

[0089] When the liquefaction controller 103 determines that the IGV opening degree θ is the first opening degree θ1, it outputs an open command to the extraction air amount control valve 52, as in the first embodiment. As a result, the extraction air amount control valve 52 opens, and the extraction process S2 is performed. In this extraction process S2, the compressed air CA in the intermediate casing 4 flows into the liquefaction system 60a via the extraction line 51.

[0090] When the liquefaction controller 103 determines that the IGV opening degree θ is the first opening degree θ1, it drives the liquefaction system 60a. As a result, the liquefaction process S3 is executed in the same manner as in the first embodiment. In this liquefaction step S3, first, the compressed air CA is cooled by heat exchange with a cooling medium such as seawater in the primary cooler 62a.

[0091] The compressed air CA cooled by the primary cooler 62a is compressed by the boost compressor 64 to become high-compressed air HCA. This high-compressed air HCA is heat exchanged with a cooling medium such as seawater in the tertiary cooler 66 and cooled. A part of the high-compressed air HCA cooled by the tertiary cooler 66 flows into the expansion turbine 65 via the high-compressed air branch line 68b. This high-compressed air HCA is adiabatically expanded in the expansion turbine 65 to become low-temperature, low-pressure air LLA. The low-temperature, low-pressure air LLA flows into the quaternary cooler 67 via the low-temperature, low-pressure air main line 69m. In addition, in this liquefaction step S3, the heating liquid air pump 84 of the first heating device 81 is driven, and the heating liquid air control valve 85 of the first heating device 81 is opened. As a result, the liquid air LA in the gas-liquid tank 82 of the first heating device 81 flows into the quaternary cooler 67. Therefore, in the quaternary cooler (first cooling heat exchanger) 67, the liquid air LA from the gas-liquid tank 82 and the low-temperature, low-pressure air LLA from the low-temperature, low-pressure air main line 69m exchange heat with another part of the high-compressed air HCA, and the other part of the high-compressed air HCA is cooled, and at least a part of it becomes liquid air LA. This liquid air LA flows into the gas-liquid mixing line 74 together with the high-compressed air HCA that was not liquefied in the quaternary cooler 67. The fluid that flows into the gas-liquid mixing line 74 is adiabatically expanded by the expansion valve 75 provided in this gas-liquid mixing line 74, and liquefaction is promoted. The liquid air LA from the gas-liquid tank 82 is heated and vaporized by heat exchange with the high-compressed air HCA in the quaternary cooler (first heater, first heating heat exchanger) 67, and returns to the gas-liquid tank 82. Therefore, in this liquefaction process S3, the liquid air LA in the gas-liquid tank 82 gradually decreases, and the vaporized air VA in the gas-liquid tank 82 gradually increases. That is, in this liquefaction step S3, a vaporization step S4 is also carried out in which the liquid air LA is vaporized to generate vaporized air VA. In addition, the low-temperature low-pressure air LLA from the expansion turbine 65 is heated by heat exchange with the highly compressed air HCA in the quaternary cooler 67, and then released into the atmosphere.

[0092] The fluid whose liquefaction has been promoted by the expansion valve 75 flows into the gas-liquid separation tank 77 and is separated into gaseous air and liquid air LA. The liquid air LA in the gas-liquid separation tank 77 flows into the liquid air tank 53 via the liquid air supply line 78.

[0093] When the IGV opening degree θ is the first opening degree θ1, the above-described extraction process S2, liquefaction process S3, and vaporization process S4 are continuously performed.

[0094] As described above, when the IGV opening θ is the first opening θ1, as in the first embodiment, the compressed air CA inside the intermediate casing 4 is extracted, and the flow rate of the compressed air CA flowing from inside the intermediate casing 4 into the combustor 17 is reduced. As a result, the flow rate of the combustion gas generated in the combustor 17 is reduced compared to when the compressed air CA inside the intermediate casing 4 is not extracted, and the gas turbine output is reduced.

[0095] When the liquefaction controller 103 determines that the IGV opening degree θ is not the first opening degree θ1, it closes the extraction amount control valve 52 to stop the extraction process S2 and stops the liquefaction system 60a to stop the liquefaction process S3.

[0096] When the liquefaction controller 103 determines that the IGV opening degree θ is the second opening degree θ2, it outputs an open command to the return amount adjustment valve 57 and outputs a drive command to the liquid air pump 56. As a result, the return amount adjustment valve 57 opens, the liquid air pump 56 is driven, and the return process S5 is performed.

[0097] When the return amount control valve 57 opens and the liquid air pump 56 is driven, the liquid air LA in the liquid air tank 53 flows into the gas-liquid tank 82 through the liquid air line 55 in the return air line 54a. As a result, the amount of liquid air LA in the gas-liquid tank 82 increases, and the vaporized air VA in the gas-liquid tank 82 is pushed out by this liquid air LA. The temperature of this vaporized air VA is lower than the temperature of the air sucked by the compressor 10. This vaporized air VA flows into the air flow path of the compressor 10 through the vaporized air line 58a in the return air line 54a. For this reason, the average temperature of the air flowing through the air flow path of the compressor 10 decreases. Even if the volumetric flow rate of the air flowing through the air flow path does not change, if the average temperature of the air flowing through the air flow path decreases, the mass flow rate of the air flowing through this air flow path increases.

[0098] In this embodiment, the heating step S6 of heating the vaporized air VA in the first embodiment is not performed. However, a heater may be provided to heat the liquid air LA in the liquid air tank 53 to about 5 to 15°C, and the heating step may be performed using this heater.

[0099] As described above, when the IGV aperture θ is the second aperture θ2, the cold vaporized air VA flows into the air passage of the compressor 10, increasing the mass flow rate of the air flowing through the air passage. As a result, in this embodiment, the mass flow rate of the combustion gas generated in the combustor 17 is greater than when the cold vaporized air VA does not flow into the air passage of the compressor 10, and the gas turbine output increases.

[0100] As described above, in this embodiment, when the IGV opening θ is the first opening θ1, the compressed air CA in the intermediate casing 4 is extracted to reduce the gas turbine output, and when the IGV opening θ is the second opening θ2, the cold vaporized air VA is caused to flow into the air flow path of the compressor 10 to increase the gas turbine output. Therefore, in this embodiment, gas turbine output adjustment can be flexibly performed and load fluctuations in the power system can be flexibly accommodated.

[0101] Also in this embodiment, in the liquefaction step S3, the compressed air CA is cooled using low-temperature thermal energy obtained in the vaporization step S4. Also in this embodiment, in the vaporization step S4, the liquid air LA is vaporized using high-temperature thermal energy obtained in the liquefaction step S3. Therefore, also in this embodiment, it is possible to reduce the amount of thermal energy supplied from outside the liquefaction equipment 50a.

[0102] In the example described above, the return air RA is guided to a flow path portion in the air flow path in the compressor casing 14, through which air flows before the intake air amount is adjusted by the IGV 15. That is, in the example described above, the return air RA is guided to a flow path portion Dau on the axial upstream side of the guide vanes 15v of the IGV 15 in the air flow path in the compressor casing 14. However, the return air RA may be guided to a flow path portion in the air flow path in the compressor casing 14, through which air flows after the intake air amount is adjusted by the IGV 15. That is, the return air RA may be guided to a flow path portion Dad on the axial downstream side of the guide vanes 15v of the IGV 15 in the air flow path in the compressor casing 14. In this case, as shown by the two-dot dashed line in FIG. 4, the vaporized air line 58aa is connected to a plurality of stator vanes 12v constituting any one of the plurality of stator vane rows 12t of the compressor 10. 5, in each of the plurality of stator vanes 12v to which the vaporized air line 58aa is connected, a plurality of air passages 13 are formed, which pass through the stator vane 12v, communicate with the vaporized air line 58aa, and open on the surface of the stator vane 12v. One of the plurality of air passages 13 opens in the surface of the stator vane 12v near the leading end 12f of the stator vane 12v, and the other air passages 13 open in the surface of the stator vane 12v at the trailing end 12r of the stator vane 12v.

[0103] As described above, when the return air RA is guided to the stator vane 12v of the compressor 10, the return air RA may be liquid air LA. In this case, as shown by the two-dot dashed line in Fig. 4, the liquid air line 55a of the return air line 54aa is connected to the stator vane 12v of the compressor 10. In this case, the return air line 54aa does not need to have a vaporized air line.

[0104] Here, the return air RA is discharged into the air flow path of the compressor from the vicinity of the front end 12f and the rear end 12r of the stator vane 12v. However, the return air RA may be discharged into the air flow path of the compressor only from the rear end 12r of the stator vane 12v. By discharging the return air RA only from the rear end 12r of the stator vane 12v in this manner, turbulence of the air flow around the stator vane 12v can be suppressed. In particular, when liquid air LA is sent to the stator vane 12v as the return air RA, it is preferable to discharge the return air RA only from the rear end 12r of the stator vane 12v.

[0105] "Third embodiment" Next, a third embodiment of a gas turbine plant according to the present disclosure will be described with reference to FIG.

[0106] 6, like the gas turbine plant of the first embodiment, the gas turbine plant of this embodiment includes a gas turbine 1, a GT generator 38, a GT power supply facility 39, a turbine cooling device 30, a waste heat utilization facility 40, a liquefaction facility 50b, and a control device 100. However, the liquefaction facility 50b of this embodiment is different from the liquefaction facility 50 of the first embodiment.

[0107] The liquefaction equipment 50b of this embodiment includes an extraction line 51, an extraction amount control valve 52, a liquefaction system 60, a liquid air tank 53, a heating system 80b, a return air line 54b, a liquid air pump 56, and a return amount control valve 57, similar to the liquefaction equipment 50 of the first embodiment. However, in this embodiment, the return destination of the return air RA through the return air line 54b is different from that of the first embodiment. Therefore, the heating system 80b of this embodiment is different from the heating system 80 of the first embodiment.

[0108] The return air line 54b of this embodiment has a liquid air line 55 and a vaporized air line 58b, similar to the return air line 54 of the first embodiment. The vaporized air line 58b is connected to the main cooling air line 33m of the turbine cooling device 30, which is different from the vaporized air line 58 of the first embodiment. In this case, the main cooling air line 33m of the turbine cooling device 30, the combustor cooling air line 33c, the moving blade cooling air line 33b, and the stationary blade cooling air line 33v all constitute a part of the return air line 54b. Therefore, in this embodiment, the return air RA is guided to the high-temperature parts of the gas turbine 1. In order to send the return air RA to the high-temperature parts of the gas turbine 1, a compressor may be provided in the vaporized air line 58b as necessary to boost the return air RA in the vaporized air line 58b. In the first embodiment, the return air RA is guided to the compressed air CA flowing into the combustor 17, but in this embodiment, the return air RA is guided to the high-temperature parts in order to cool them. Therefore, the temperature of the return air RA in this embodiment may be lower than the temperature of the return air RA in the first embodiment. Therefore, the heating system 80b in this embodiment is different from the heating system 80 in the first embodiment, as described above.

[0109] The heating system 80b of the present embodiment includes a first heating device 81 capable of heating the liquid air LA from the liquid air tank 53 to generate vaporized air VA, and a second heating device 88 capable of heating the vaporized air VA. However, the heating system 80b of the present embodiment does not include the third heating device 95 in the heating system 80 of the first embodiment. Therefore, the vaporized air line 58b of the present embodiment is not provided with the tertiary heater 96 in the first embodiment.

[0110] The liquefaction system 60 of this embodiment is the same as the liquefaction system 60 of the first embodiment. Therefore, the liquefaction system 60 of this embodiment has a primary cooler (second cooling heat exchanger) 61, a secondary cooler 62, a cooling device 63, a gas-liquid separation tank 77, a liquid air supply line 78, and a liquid air supply control valve 79.

[0111] The liquefaction controller 103 of the control device 100 monitors whether the IGV opening degree θ is the first opening degree θ1 or the second opening degree θ2, as in the first embodiment.

[0112] When the liquefaction controller 103 determines that the IGV opening θ is the first opening θ1, it outputs an open command to the extraction air amount control valve 52, as in the first embodiment. As a result, the extraction air amount control valve 52 opens, and the extraction process S2 is performed. In this extraction process S2, the compressed air CA in the intermediate casing 4 flows into the liquefaction system 60 via the extraction line 51. When the liquefaction controller 103 further determines that the IGV opening θ is the first opening θ1, it drives the liquefaction system 60. As a result, as in the first embodiment, the liquefaction process S3 and the vaporization process S4 are performed.

[0113] When the IGV opening degree θ is the first opening degree θ1, the above-described extraction process S2, liquefaction process S3, and vaporization process S4 are continuously performed.

[0114] As described above, when the IGV opening θ is the first opening θ1, as in the first embodiment, the compressed air CA inside the intermediate casing 4 is extracted, and the flow rate of the compressed air CA flowing from inside the intermediate casing 4 into the combustor 17 is reduced. As a result, the flow rate of the combustion gas generated in the combustor 17 is reduced compared to when the compressed air CA inside the intermediate casing 4 is not extracted, and the gas turbine output is reduced.

[0115] When the liquefaction controller 103 determines that the IGV opening degree θ is not the first opening degree θ1, it closes the extraction amount control valve 52 to stop the extraction process S2 and stops the liquefaction system 60 to stop the liquefaction process S3.

[0116] When the liquefaction controller 103 determines that the IGV opening degree θ is the second opening degree θ2, it outputs an open command to the return amount adjustment valve 57 and outputs a drive command to the liquid air pump 56 and the heating system 80b. As a result, the return amount adjustment valve 57 opens, the liquid air pump 56 and the heating system 80b are driven, and the return process S5 and the heating process S6 are performed.

[0117] In the return step S5, the liquid air LA in the liquid air tank 53 flows into the gas-liquid tank 82 through the liquid air line 55 in the return air line 54b. As a result, the amount of the liquid air LA in the gas-liquid tank 82 increases, and the vaporized air VA in the gas-liquid tank 82 is pushed out by this liquid air LA. This vaporized air VA flows into the secondary heater 91 through the vaporized air line 58b in the return air line 54b. The heat storage material HG heated in the liquefaction step S3 also flows into the secondary heater 91 from the heat storage tank 89. As a result, in the secondary heater (second heating heat exchanger) 91, heat is exchanged between the heated heat storage material HG and the vaporized air VA, and the heat storage material HG is cooled while the vaporized air VA is heated (heating step S6). The cooled heat storage material HG passes through the primary cooler (second cooling heat exchanger) 61 and then returns to the heat storage tank 89. On the other hand, the vaporized air VA heated by heat exchange with the heat storage material HG flows into the high-temperature parts of the gas turbine 1 via the vaporized air line 58b of the return air line 54b.

[0118] When the IGV opening degree θ is the second opening degree θ2, the above-described return process S5 and heating process S6 are continuously executed.

[0119] As described above, in this embodiment, when the IGV aperture θ is the second aperture θ2, the evaporated air VA from the liquefaction facility 50b flows into the high-temperature components of the gas turbine 1, and at this time, it is possible to eliminate or reduce the amount of compressed air CA extracted from the gas turbine 1 by the turbine cooling device 30. As a result, the output for driving the compressor 10 by the turbine 20 is suppressed, and the gas turbine output is increased.

[0120] As described above, in this embodiment, when the IGV opening θ is the first opening θ1, the compressed air CA in the intermediate casing 4 is extracted to reduce the gas turbine output, and when the IGV opening θ is the second opening θ2, the vaporized air VA is caused to flow into the high-temperature components to increase the gas turbine output. Therefore, in this embodiment, gas turbine output adjustment can be flexibly performed, and load fluctuations in the power system can be flexibly responded to.

[0121] In this embodiment, similar to the first embodiment, in the liquefaction step S3, the compressed air CA is cooled using low-temperature thermal energy obtained in the evaporation step S4 and the heating step S6. Also, in this embodiment, similar to the first embodiment, in the evaporation step S4 and the heating step S6, the liquid air LA and the vaporized air VA are heated using high-temperature thermal energy obtained in the liquefaction step S3. Therefore, in this embodiment, too, it is possible to reduce the amount of thermal energy supplied from outside the liquefaction equipment 50b.

[0122] "Fourth embodiment" Next, a fourth embodiment of a gas turbine plant according to the present disclosure will be described with reference to FIG.

[0123] 7, the gas turbine plant of this embodiment, like the gas turbine plant of the first embodiment, includes a gas turbine 1, a GT generator 38, a GT power supply facility 39, a turbine cooling device 30, a waste heat utilization facility 40, a liquefaction facility 50c, and a control device 100. However, the liquefaction facility 50c of this embodiment is different from the liquefaction facility 50 of the first embodiment.

[0124] The liquefaction equipment 50c of this embodiment, like the liquefaction equipment 50 of the first embodiment, includes an extraction line 51, an extraction amount control valve 52, a liquefaction system 60c, a liquid air tank 53, a heating system 80c, a return air line 54, a liquid air pump 56, and a return amount control valve 57.

[0125] The liquefaction system 60c includes a primary cooler 61, a secondary cooler 62c, a cooling device 63c, a gas-liquid separation tank 77, a liquid air supply line 78, and a liquid air supply control valve 79. The primary cooler 61 and the secondary cooler 62c are provided in the extraction line 51. The primary cooler 61, like the primary cooler 61 of the first embodiment, can cool the compressed air CA by exchanging heat between the compressed air CA and the heat storage material HG. The secondary cooler 62c corresponds to the quaternary cooler 67 of the first embodiment, and can exchange heat between the compressed air CA cooled by the primary cooler 61 and the liquid air LA. The cooling device 63c of this embodiment does not include an expansion turbine 65 or the like, unlike the above embodiments. The cooling device 63c of this embodiment has a liquefied gas tank 70 capable of storing liquefied gas, a first cooling heat exchanger 71 capable of exchanging heat between the compressed air CA cooled by the secondary cooler 62c and the liquefied gas, a liquefied gas line 72 connecting the liquefied gas inlet of the first cooling heat exchanger 71 to the liquefied gas tank 70, and a liquefied gas pump 72p and a liquefied gas control valve 72v provided in the liquefied gas line 72.

[0126] The compressed air CA cooled by the first cooling heat exchanger 71 becomes liquid air LA, and is sent to the liquid air tank 53. Note that the expansion valve 75 and the gas-liquid separation tank 77 in the first embodiment may be provided between the first cooling heat exchanger 71 and the liquid air tank 53.

[0127] The heating system 80c of this embodiment includes a first heating device 81 capable of heating liquid air LA from the liquid air tank 53 to generate vaporized air VA, a second heating device 88 capable of heating the vaporized air VA from the first heating device 81, and a third heating device 95 capable of heating the vaporized air VA from the second heating device 88.

[0128] The first heating device 81 has a gas-liquid tank 82 capable of storing liquid air LA and vaporized air VA formed by vaporizing the liquid air LA, a primary heater (first heating heat exchanger) 62c, a heating liquid air line 83, a vaporized air return line 86, a heating liquid air pump 84, and a heating liquid air control valve 85.

[0129] The heating liquid air line 83 connects the liquid air outlet of the gas-liquid tank 82 and the liquid air inlet of the primary heater 62c. A heating liquid air pump 84 and a heating liquid air adjustment valve 85 are provided in this heating liquid air line 83. The vaporized air return line 86 connects the vaporized air outlet of the primary heater 62c and the vaporized air inlet of the gas-liquid tank 82. As in the first embodiment, the first heating device 81 executes the vaporization process S4 of vaporizing the liquid air LA.

[0130] The primary heater (first heating heat exchanger) 62c is a heat exchanger that exchanges heat between the compressed air CA and the liquid air LA, and also serves as the above-mentioned secondary cooler 62c.

[0131] The second heating device 88 is the same as the second heating device 88 in the first embodiment. Moreover, the third heating device 95 is the same as the third heating device 95 in the first embodiment.

[0132] The liquefaction controller 103 of the control device 100 monitors whether the IGV opening degree θ is the first opening degree θ1 or the second opening degree θ2, as in the above-described embodiments.

[0133] When the liquefaction controller 103 determines that the IGV opening θ is the first opening θ1, the extraction process S2, the liquefaction process S3, and the vaporization process S4 are executed as in the first embodiment. However, the liquefaction process S3 in this embodiment includes a process of cooling the compressed air CA by exchanging heat between the liquefied gas in the liquefied gas tank 70 and the compressed air CA that has flowed through the extraction line 51. In addition, when the liquefaction controller 103 determines that the IGV opening θ is the second opening θ2, the heating process S6 of the air vaporized in the vaporization process S4 is executed as in the first embodiment.

[0134] As described above, in this embodiment as well, when the IGV opening θ is the first opening θ1, the compressed air CA in the intermediate casing 4 is extracted to reduce the gas turbine output, and when the IGV opening θ is the second opening θ2, the cold vaporized air VA is caused to flow into the air flow path of the compressor 10 to increase the gas turbine output. Therefore, in this embodiment as well, gas turbine output adjustment can be flexibly performed and load fluctuations in the power system can be flexibly responded to.

[0135] In this embodiment, the compressed air CA is cooled in the liquefaction step S3 using low-temperature thermal energy obtained in the vaporization step S4. Also, in this embodiment, the liquid air LA is vaporized in the vaporization step S4 using high-temperature thermal energy obtained in the liquefaction step S3. Therefore, in this embodiment, the amount of thermal energy supplied from outside the liquefaction equipment 50c can be reduced.

[0136] In this embodiment, when the compressed air CA needs to be further compressed in order to liquefy the compressed air CA, the boost compressor 64 of the first embodiment may be provided.

[0137] Furthermore, although this embodiment is a modification of the first embodiment, the cooling device 63 of the second embodiment and the cooling device 63 of the third embodiment may be configured similarly to the cooling device 63c of this embodiment.

[0138] "Variations" In the first embodiment, when return air RA is supplied from the liquefaction equipment 50 into the intermediate casing 4, or in the second embodiment, when return air RA is supplied from the liquefaction equipment 50a into the air flow path of the compressor casing 14, the fuel control device 101 may increase the fuel flow rate in accordance with the flow rate of the return air RA, provided that the following conditions a, b, and c are satisfied. a. The fuel burns stably in the combustor 17. b. The combustion gas (exhaust gas) flowing out from the combustor 17 does not exceed various regulatory values ​​for this combustion gas. c. The maximum allowable temperature of the combustion gases specified for the protection of high-temperature components must not be exceeded.

[0139] In the above embodiment, during the liquefaction process S3, a vaporization process S4 is also performed in which the liquid air LA is vaporized by heat obtained by cooling the compressed air CA. However, when heat exchange between the compressed air CA and the liquid air LA is not performed, the vaporization process S4 may be performed in parallel with the heating process S6.

[0140] The liquefaction system of each of the above embodiments includes a plurality of coolers, but the number of coolers is not limited to the number exemplified in each of the above embodiments. Also, the heating system of each of the above embodiments includes one or more heaters, but the number of heaters is not limited to the number exemplified in each of the above embodiments.

[0141] Furthermore, the liquefaction system of each of the above embodiments may be provided with an argon separator that separates argon from the compressed air. For example, as in a liquefaction system 60d shown in Fig. 8, an argon separator 110 may be provided upstream of the gas-liquid separation tank 77 in the compressed air flow.

[0142] The argon separator 110 separates argon from the compressed air by cryogenic separation. The cryogenic separation is a method of separating a specific type of gas by utilizing the difference in boiling point of each of a plurality of types of gases constituting the compressed air. For example, the boiling point of oxygen is −183° C., the boiling point of argon is −185.8° C., and the boiling point of nitrogen is −195.8° C. In the example shown in FIG. 8, the argon separator 110 separates argon from the compressed air by cryogenic separation. That is, as shown in FIG. 9, the liquefaction step S3a includes an argon separation step S3aa, and in this argon separation step S3aa, argon in the exhaust gas is separated by cryogenic separation. The argon separated by the argon separator 110 is sent to, for example, an argon recovery tank 111. The compressed air from which argon has been removed is further cooled and then sent to the gas-liquid separation tank 77 via the expansion valve 75, or is sent directly to the gas-liquid separation tank 77 via the expansion valve 75. The main components of the compressed air from which argon has been removed are nitrogen and oxygen.

[0143] The gas turbine plant of each of the above embodiments includes two generators: a GT generator 38 that generates electricity by driving the gas turbine 1, and an ST generator 48 that generates electricity by driving the steam turbine 43. However, the gas turbine plant may include only one generator. In this case, the one generator can generate electricity by driving either the gas turbine 1 or the steam turbine 43.

[0144] The gas turbine plant in each of the above embodiments includes the exhaust heat utilization facility 40. However, the gas turbine plant does not necessarily need to include the exhaust heat utilization facility 40.

[0145] The gas turbine plant in each of the above embodiments is a gas turbine plant as a completed plant. If the gas turbine plant does not include the liquefaction equipment and the liquefaction controller in each of the above embodiments, the gas turbine plant may be modified by executing a process of adding the liquefaction equipment and the liquefaction controller in each of the above embodiments. Since the control device 100 in the gas turbine plant in each of the above embodiments is a computer, when the liquefaction controller 103 is added in the modification of the gas turbine plant, a program that causes the computer to function as the liquefaction controller 103 may be installed in the computer.

[0146] "Additional Notes" The gas turbine plants in the above-described embodiment and modified examples can be understood, for example, as follows.

[0147] (1) A gas turbine plant according to a first aspect, The gas turbine 1 includes a compressor 10 capable of compressing air, a combustor 17 capable of burning fuel in compressed air CA, which is air compressed by the compressor 10, to generate combustion gas, and a turbine 20 capable of being driven by the combustion gas, liquefaction equipment 50, 50a, 50b, 50c capable of liquefying gaseous air, and a liquefaction controller 103 for controlling the liquefaction equipment 50, 50a, 50b, 50c. The compressor 10 includes a compressor rotor 11 rotatable about an axis, a compressor casing 14 covering the outer periphery of the compressor rotor 11, a plurality of stator vanes 12v provided on the inner periphery of the compressor casing 14, and an intake air amount regulator 15 capable of adjusting the intake air amount, which is the flow rate of air flowing into the compressor casing 14, by opening and closing the compressor casing 14. The liquefaction equipment 50, 50a, 50b, 50c includes an extraction line 51 capable of extracting a portion of the compressed air CA from the compressor 10, a liquefaction system 60, 60a, 60c capable of liquefying the compressed air CA flowing through the extraction line 51, an extraction amount control valve 52 capable of adjusting the flow rate of the compressed air CA flowing through the extraction line 51, a liquid air tank 53 capable of storing liquid air LA, which is the compressed air CA liquefied in the liquefaction system 60, 60a, 60c, and the liquid air tank 54. The gas turbine has return air lines 54, 54a, 54aa, 54b that can guide the liquid air LA in the tank 53 or return air RA, which is vaporized air VA from the liquid air LA, to a flow path through which air or compressed air CA flows in the gas turbine 1, or to high-temperature components that come into contact with the combustion gas among the components that constitute the gas turbine 1, and a return amount control valve 57 that can adjust the flow rate of the return air RA flowing through the return air lines 54, 54a, 54aa, 54b. The liquefaction controller 103 opens the extraction amount control valve 52 to guide the compressed air CA to the liquefaction systems 60, 60a, 60c when the opening of the intake air amount regulator 15 is a first opening amount θ1 or when a parameter correlated with the opening amount has a value corresponding to the first opening amount θ1, and opens the return amount control valve 57 to guide the return air RA to the gas turbine 1 when the opening of the intake air amount regulator 15 is a second opening amount θ2 which is larger than the first opening amount θ1 or when the parameter has a value corresponding to the second opening amount θ2.The first opening θ1 is an opening when the amount of intake air flowing into the compressor casing 14 is made smaller than the amount of intake air when the output of the gas turbine 1 is the rated output.

[0148] In this embodiment, at the first opening θ1 when the intake air amount is made smaller than the intake air amount when the output of the gas turbine 1 is at the rated output, a part of the compressed air CA from the compressor 10 is extracted to the liquefaction equipment 50, 50a, 50b, 50c. This reduces the flow rate of the compressed air CA flowing from inside the intermediate casing 4 into the combustor 17. Therefore, in this embodiment, at the first opening θ1, the flow rate of the combustion gas generated in the combustor 17 is smaller than when the compressed air CA is not extracted from the compressor 10, and the gas turbine output is reduced.

[0149] In this embodiment, when the second opening θ2 is set to a larger opening than the first opening θ1, the liquid air LA in the liquid air tank 53 or the return air RA, which is the air obtained by vaporizing the liquid air LA, is guided to a flow path through which the air or compressed air CA flows in the gas turbine 1, or to a high-temperature component that comes into contact with the combustion gas among the components constituting the gas turbine 1. For example, when the second opening θ2 is set, when the return air RA is guided to a flow path through which the air or compressed air CA flows in the gas turbine 1, the flow rate of the combustion gas generated in the combustor 17 is larger than when the return air RA is not guided to this flow path, and the gas turbine output is increased. When the second opening θ2 is set, when the return air RA is guided to a high-temperature component of the gas turbine 1, the flow rate of the compressed air CA for cooling the high-temperature component is smaller than when the return air RA is not guided to the high-temperature component, and the flow rate of the air flowing into the combustor 17 is larger, and the gas turbine output is increased.

[0150] Therefore, in this aspect, gas turbine output adjustment can be flexibly performed, and load fluctuations in the power system can be flexibly dealt with.

[0151] (2) A gas turbine plant according to a second aspect of the present invention comprises: In the gas turbine plant in the first aspect, the first opening θ1 is a minimum opening min that can minimize the amount of intake air flowing into the compressor casing 14.

[0152] (3) A gas turbine plant according to a third aspect, In the gas turbine plant in the first embodiment or the second embodiment, the second opening θ2 is a maximum opening max that can maximize the amount of intake air flowing into the compressor casing 14.

[0153] (4) A gas turbine plant according to a fourth aspect comprises: In the gas turbine plant according to any one of the first to third aspects, the liquefaction system 60, 60a includes a cooling device 63 capable of cooling the compressed air CA from the extraction line 51. The cooling device 63 includes a boost compressor 64 capable of further compressing the compressed air CA from the extraction line 51 to generate high-compressed air HCA, an expansion turbine 65 capable of adiabatically expanding a portion of the high-compressed air HCA to generate low-temperature, low-pressure air LLA, and a first cooling heat exchanger 67 capable of exchanging heat between another portion of the high-compressed air HCA and the low-temperature, low-pressure air LLA to cool the high-compressed air HCA.

[0154] (5) A gas turbine plant according to a fifth aspect comprises: In the gas turbine plant according to any one of the first to third aspects, the liquefaction system 60c includes a cooling device 63c capable of cooling the compressed air CA from the extraction line 51. The cooling device 63c includes a liquefied gas tank 70 capable of storing liquefied gas, and a first cooling heat exchanger 71 capable of cooling the compressed air CA by exchanging heat between the compressed air CA flowing through the extraction line 51 and the liquefied gas.

[0155] (6) A gas turbine plant according to a sixth aspect, In the gas turbine plant in the fourth or fifth aspect, the liquefaction facilities 50, 50a, 50b, 50c include heating systems 80, 80a, 80b, 80c that heat the liquid air LA from the liquid air tank 53.

[0156] (7) A gas turbine plant according to a seventh aspect comprises: In the gas turbine plant of the sixth aspect, the heating systems 80, 80a, 80b, 80c include first heating devices 81, 81c capable of heating the liquid air LA from the liquid air tank 53 and generating vaporized air VA by vaporizing the liquid air LA.

[0157] (8) In an eighth aspect, a gas turbine plant includes: In the gas turbine plant of the seventh aspect, the first heating device 81, 81c includes a gas-liquid tank 82 capable of storing the liquid air LA and the vaporized air VA, and a first heating heat exchanger 67, 62c capable of exchanging heat between the liquid air LA in the gas-liquid tank 82 and the compressed air CA, heating the liquid air LA and returning the liquid air LA to the gas-liquid tank 82 as the vaporized air VA, while cooling the compressed air CA. The liquefaction system 60, 60a, 60c includes the first heating heat exchanger 67, 62c as a cooling heat exchanger capable of cooling the compressed air CA.

[0158] In this embodiment, in the process of cooling the compressed air CA in the liquefaction system 60, 60a, 60c, the compressed air CA can be cooled using low-temperature thermal energy obtained in the process of heating the liquid air LA or vaporized air VA in the heating system 80, 80a, 80b, 80c. Also, in this embodiment, in the process of heating the liquid air LA or vaporized air VA in the heating system 80, 80a, 80b, 80c, the liquid air LA or vaporized air VA can be heated using high-temperature thermal energy obtained in the process of cooling the compressed air CA in the liquefaction system 60, 60a, 60c. Therefore, in this embodiment, the thermal energy supplied from outside the liquefaction equipment 50, 50a, 50b, 50c can be reduced.

[0159] (9) A gas turbine plant according to a ninth aspect comprises: In the gas turbine plant of the fourth embodiment, the liquefaction equipment 50, 50b includes a heating system 80, 80b that heats the liquid air LA from the liquid air tank 53. The heating system 80, 80b includes a first heating device 81 that can heat the liquid air LA from the liquid air tank 53 and generate vaporized air VA in which the liquid air LA is vaporized. The first heating device 81 includes a gas-liquid tank 82 capable of storing the liquid air LA and the vaporized air VA, and a first heating heat exchanger 67 capable of exchanging heat between the liquid air LA from the gas-liquid tank 82 and the other part of the highly compressed air HCA from the boost compressor 64 to heat the liquid air LA and return the liquid air LA to the gas-liquid tank 82 as the vaporized air VA, while cooling the other part of the highly compressed air HCA. The liquefaction system 60 includes the first heating heat exchanger 67 as the first cooling heat exchanger 67. The first heating heat exchanger 67 as the first cooling heat exchanger 67 is capable of exchanging heat between the liquid air LA from the gas-liquid tank 82 and the low-temperature low-pressure air LLA from the expansion turbine 65 and the other part of the highly compressed air HCA from the boost compressor 64.

[0160] In this embodiment, in the process of cooling the compressed air CA in the liquefaction system 60, the compressed air CA can be cooled using low-temperature thermal energy obtained in the process of heating the liquid air LA or vaporized air VA in the heating systems 80, 80b. Also, in this embodiment, in the process of heating the liquid air LA or vaporized air VA in the heating systems 80, 80b, the liquid air LA or vaporized air VA can be heated using high-temperature thermal energy obtained in the process of cooling the compressed air CA in the liquefaction system 60. Therefore, in this embodiment, the thermal energy supplied from outside the liquefaction equipment 50, 50b can be reduced.

[0161] (10) A gas turbine plant in a tenth aspect comprises: In the gas turbine plant according to any one of the seventh to ninth aspects, the heating systems 80, 80b, 80c include a second heating device 88 capable of heating the vaporized air VA from the first heating device 81.

[0162] (11) In an eleventh aspect, a gas turbine plant comprises: In the gas turbine plant in the tenth embodiment, the liquefaction system 60, 60c has a second cooling heat exchanger 61 capable of heating the heat storage material HG by heat exchange between the compressed air CA before reaching the cooling device 63, 63c and the heat storage material HG, while cooling the compressed air CA. The second heating device 88 has a heat storage tank 89 capable of storing the heat storage material HG heated by the second cooling heat exchanger 61, and a second heating heat exchanger 91 capable of heating the vaporized air VA by heat exchange between the heat storage material HG from the heat storage tank 89 and the vaporized air VA from the first heating device 81, while cooling the heat storage material HG. The second cooling heat exchanger 61 is capable of heat exchange between the compressed air CA before reaching the cooling device 63 and the heat storage material HG cooled by the second heating heat exchanger 91.

[0163] In this embodiment, in the process of cooling the compressed air CA in the liquefaction system 60, 60c, the compressed air CA can be cooled using low-temperature thermal energy obtained in the process of heating the vaporized air VA in the heating system 80, 80b, 80c. Also, in this embodiment, in the process of heating the vaporized air VA in the heating system 80, 80b, 80c, the liquid air LA and the vaporized air VA can be heated using high-temperature thermal energy obtained in the process of cooling the compressed air CA in the liquefaction system 60, 60c. Therefore, in this embodiment, the thermal energy supplied from outside the liquefaction equipment 50, 50b, 50c can be reduced.

[0164] (12) A gas turbine plant according to a twelfth aspect comprises: In the gas turbine plant in the eleventh aspect, the heating system 80, 80c includes a third heating device 95 capable of heating the vaporized air VA from the second heating device 88. The return air line 54 is capable of directing the evaporated air VA heated by the third heating device 95 as the return air RA to the flow path in the gas turbine 1 through which the compressed air CA flows.

[0165] In this embodiment, when the second opening θ2 is set to a value larger than the first opening θ1, the temperature of the return air RA that is guided to the flow passage through which the compressed air CA flows in the gas turbine 1 can be increased. Therefore, in this embodiment, the temperature of the air flowing into the combustor 17 is higher than in the case where the return air RA is not heated by the third heating device 95, and the gas turbine output is increased.

[0166] (13) A gas turbine plant according to a thirteenth aspect comprises: The gas turbine plant in the twelfth aspect includes a heat recovery boiler 41 capable of generating steam by utilizing heat of exhaust gas, which is a combustion gas exhausted from the gas turbine 1. The third heating device 95 has a third heating heat exchanger 96 capable of heating the vaporized air VA by exchanging heat between the vaporized air VA from the second heating device 88 and the steam from the heat recovery boiler 41.

[0167] In this embodiment, the vaporized air VA can be heated by using high-temperature thermal energy obtained in the gas turbine plant, and therefore the amount of thermal energy supplied from outside the gas turbine plant can be reduced.

[0168] (14) A gas turbine plant in a fourteenth aspect comprises: In a gas turbine plant in any one of the first to thirteenth embodiments, the liquefaction system 60d has an argon separator 110 capable of cryogenically separating argon in the compressed air CA during the liquefaction process of the compressed air CA in the liquefaction system 60d.

[0169] In this embodiment, argon can be separated from the compressed air CA during the liquefaction process of the compressed air CA.

[0170] (15) In a fifteenth aspect, the gas turbine plant comprises: In a gas turbine plant in any one of the first to fourteenth aspects, the return air line 54 is capable of directing the return air RA to a flow path through which the compressed air CA flows in the gas turbine 1.

[0171] In this embodiment, when the second opening θ2 is set to a value larger than the first opening θ1, the return air RA can be guided to the flow path through which the compressed air CA flows in the gas turbine 1. Therefore, in this embodiment, the flow rate of the combustion gas generated in the combustor 17 becomes larger than when the return air RA is not guided to this flow path, and the gas turbine output increases.

[0172] (16) A gas turbine plant according to a sixteenth aspect, In a gas turbine plant in any one of the first to eleventh embodiments, the return air line 54a, 54aa is capable of directing the return air RA into an air flow path through which air flows within the compressor casing 14.

[0173] In this embodiment, at the second opening θ2, which is larger than the first opening θ1, the return air RA can be guided to the air flow path in the compressor casing 14. Therefore, at the second opening θ2, the average temperature of the air flowing through the air flow path decreases. Even if the volumetric flow rate of the air flowing through the air flow path does not change, if the average temperature of the air flowing through the air flow path decreases, the mass flow rate of the air flowing through the air flow path increases. Therefore, in this embodiment, at the second opening θ2, the mass flow rate of the combustion gas generated in the combustor 17 becomes larger than when the cold vaporized air VA does not flow into the air flow path of the compressor 10, and the gas turbine output increases.

[0174] (17) A gas turbine plant according to a seventeenth aspect, In the gas turbine plant in the sixteenth aspect, the return air line 54 is capable of directing the return air RA to a flow path portion in the air flow path within the compressor casing 14 through which air flows before the intake air volume is adjusted by the intake air volume adjuster 15.

[0175] (18) A gas turbine plant according to an eighteenth aspect, In the gas turbine plant of the sixteenth aspect, at least one of the plurality of stator vanes 12v of the compressor 10 is formed with an air passage 13 that passes through the stator vane 12v and opens at the surface of the stator vane 12v, and the return air line 54aa is capable of directing the return air RA into the air passage 13 within the stator vane 12v.

[0176] (19) A gas turbine plant in a nineteenth aspect comprises: In the gas turbine plant in the eighteenth aspect, the return air line 54aa can guide the liquid air LA into the air passage 13 of the stator vane 12v as the return air RA.

[0177] (20) A gas turbine plant in a twentieth aspect comprises: In the gas turbine plant according to any one of the first to ninth aspects, the high-temperature component is provided with a cooling air passage 23 that passes through the high-temperature component and opens at a surface of the high-temperature component that contacts the combustion gas. The return air line 54b is capable of guiding the return air RA to the cooling air passage 23 of the high-temperature component.

[0178] In this embodiment, at the second opening θ2 that is larger than the first opening θ1, the return air RA can be guided to the high-temperature components of the gas turbine 1. Therefore, at the second opening θ2, the flow rate of the compressed air CA for cooling the high-temperature components is smaller than when the return air RA is not guided to the high-temperature components, and the flow rate of the air flowing into the combustor 17 is increased, thereby increasing the gas turbine output.

[0179] The operation method of the gas turbine plant in the above embodiment and the modified example can be understood as follows, for example.

[0180] (21) A method for operating a gas turbine plant in a twenty-first aspect is applied to the following gas turbine plant. This gas turbine plant includes a gas turbine 1. The gas turbine 1 includes a compressor 10 capable of compressing air, a combustor 17 capable of generating combustion gas by burning fuel in compressed air CA, which is the air compressed by the compressor 10, and a turbine 20 capable of being driven by the combustion gas. The compressor 10 includes a compressor rotor 11 capable of rotating about an axis, a compressor casing 14 covering the outer periphery of the compressor rotor 11, a plurality of stator vanes 12v provided on the inner periphery of the compressor casing 14, and an intake air amount regulator 15 capable of adjusting the intake air amount, which is the flow rate of air flowing into the compressor casing 14, by opening and closing the compressor 10. The above-mentioned operating method includes an extraction process S2 of extracting a part of the compressed air CA from the compressor 10, a liquefaction process S3 of liquefying the compressed air CA extracted in the extraction process S2 to generate liquid air LA, and a return process S5 of guiding return air RA, which is the liquid air LA or vaporized air VA obtained by vaporizing the liquid air LA, to a flow path through which air or compressed air CA flows in the gas turbine 1, or to a high-temperature part that comes into contact with the combustion gas among parts constituting the gas turbine 1. The extraction process S2 and the liquefaction process S3 are executed when the opening degree of the intake air regulator 15 is a first opening degree θ1 or a parameter having a correlation with the opening degree has a value corresponding to the first opening degree θ1. The return process S5 is executed when the opening degree of the intake air regulator 15 is a second opening degree θ2 larger than the first opening degree θ1 or the parameter has a value corresponding to the second opening degree θ2. The first opening θ1 is an opening when the amount of intake air flowing into the compressor casing 14 is made smaller than the amount of intake air when the output of the gas turbine 1 is the rated output.

[0181] By carrying out the operating method of this aspect, like the gas turbine plant of the first aspect, it is possible to flexibly adjust the gas turbine output and flexibly respond to load fluctuations in the power system.

[0182] (22) A method for operating a gas turbine plant in a twenty-second aspect includes the steps of: In the gas turbine plant operation method according to the twenty-first aspect, the first opening θ1 is a minimum opening min that can minimize the amount of intake air flowing into the compressor casing 14.

[0183] (23) A method for operating a gas turbine plant in a twenty-third aspect, comprising: In the gas turbine plant operation method according to the twenty-first or twenty-second aspect, the second opening θ2 is a maximum opening max that can maximize the amount of intake air flowing into the compressor casing 14.

[0184] (24) A method for operating a gas turbine plant in a twenty-fourth aspect includes the steps of: In a method for operating a gas turbine plant in any one of the twenty-first to twenty-third aspects, the liquefaction process S3a includes an argon separation process S3aa for cryogenically separating argon in the compressed air CA during the liquefaction process of the compressed air CA.

[0185] In this embodiment, argon can be separated from the compressed air CA during the liquefaction process of the compressed air CA.

[0186] The method of modifying a gas turbine plant in the above-described embodiment and modified examples can be understood as follows, for example.

[0187] (25) The method for modifying a gas turbine plant in the twenty-fifth aspect is applied to the following gas turbine plant. This gas turbine plant includes a gas turbine 1. The gas turbine 1 includes a compressor 10 capable of compressing air, a combustor 17 capable of generating combustion gas by burning fuel in compressed air CA, which is the air compressed by the compressor 10, and a turbine 20 capable of being driven by the combustion gas. The compressor 10 includes a compressor rotor 11 capable of rotating about an axis, a compressor casing 14 covering the outer periphery of the compressor rotor 11, a plurality of stator vanes 12v provided on the inner periphery of the compressor casing 14, and an intake air amount regulator 15 capable of adjusting the intake air amount, which is the flow rate of air flowing into the compressor casing 14, by opening and closing the compressor 10. The above-mentioned retrofitting method includes a step of adding liquefaction equipment 50, 50a, 50b, 50c capable of liquefying gaseous air, and a liquefaction controller 103 for controlling the liquefaction equipment 50. The liquefaction equipment 50, 50a, 50b, 50c added in the above step includes an extraction line 51 capable of extracting a part of the compressed air CA from the compressor 10, a liquefaction system 60, 60a, 60c capable of liquefying the compressed air CA flowing through the extraction line 51, a liquid air tank 53 capable of storing liquid air LA, which is the compressed air CA liquefied in the liquefaction system 60, 60a, 60c, an extraction amount control valve 52 capable of adjusting the flow rate of the compressed air CA flowing through the extraction line 51, and The gas turbine has return air lines 54, 54a, 54aa, 54b that can guide the liquid air LA in a liquid air tank 53 or return air RA, which is vaporized air VA from the liquid air LA, to a flow path through which air or compressed air CA flows in the gas turbine 1, or to high-temperature components that come into contact with the combustion gas among the components that make up the gas turbine 1, and a return amount control valve 57 that can adjust the flow rate of the return air RA flowing through the return air lines 54, 54a, 54aa, 54b. The liquefaction controller 103 added in the process opens the extraction air amount control valve 52 to guide the compressed air CA to the liquefaction systems 60, 60a, 60c when the opening of the intake air amount regulator 15 is a first opening θ1 or a parameter correlating with the opening has a value corresponding to the first opening θ1, and opens the return amount control valve 57 to guide the return air RA to the gas turbine 1 when the opening of the intake air amount regulator 15 is a second opening θ2 that is larger than the first opening θ1 or the parameter has a value corresponding to the second opening θ2. The first opening θ1 is an opening when the amount of intake air flowing into the compressor casing 14 is made smaller than the amount of intake air when the output of the gas turbine 1 is at the rated output.

[0188] In a gas turbine plant retrofitted by the retrofit method of this embodiment, like the gas turbine plant of the first embodiment, gas turbine output adjustment can be flexibly performed and load fluctuations in the power system can be flexibly responded to.

[0189] (26) A method for modifying a gas turbine plant in a twenty-sixth aspect includes the steps of: In the method for modifying a gas turbine plant in the twenty-fifth aspect, the liquefaction system 60d has an argon separator 110 capable of cryogenically separating argon in the compressed air CA during the liquefaction process of the compressed air CA in the liquefaction system 60d.

[0190] In this embodiment, argon can be separated from the compressed air CA during the liquefaction process of the compressed air CA. [Industrial Applicability]

[0191] In one aspect of the present disclosure, gas turbine output adjustment can be flexibly performed, and load fluctuations in the power system can be flexibly accommodated. [Explanation of symbols]

[0192] 1: Gas turbine 2: Gas turbine rotor 3: Gas turbine casing 4: Intermediate casing 5: Fuel line 6: Fuel control valve 10: Compressor 11: Compressor rotor 11a: Compressor rotor shaft 11t: Moving blade row 11b: Moving blade 12t: Stator blade row 12v: static wing 12f: Front end 12r: Rear end 13: Air passage 14: Compressor casing 15: Intake volume regulator (IGV) 15v: Guide vane 15d: Driver 17: Combustor 17c: Combustion tube (or tail tube) 17n: Fuel nozzle 20: Turbine 21: Turbine rotor 21a: Turbine rotor shaft 21ap: Cooling air passage 21t: Moving blade row 21b: Moving blade 22t: Stator blade row 22v: static wing 23: Cooling air passage 24: Turbine casing 30: Turbine cooling device 31: Cooling bleed line 31v: Cooling bleed air volume control valve 32:Cooler 33: Cooling air line 33m: Main cooling air line 33c: Combustor cooling air line 33b: Blade cooling air line 33v: Stator blade cooling air line 34: Cooling air control valve 38:GT generator 39:GT power supply equipment 39a:GT power line 39b:GT circuit breaker 39t: GT transformer 39m:GT power meter 40: Waste heat utilization equipment 41: Waste heat recovery boiler 41d: Duct 41t: Heat transfer tube 42: Chimney 43: Steam turbine 44: Main steam line 45: Condenser 46: Water supply line 47: Water pump 48:ST generator 49:ST power supply equipment 49a:ST power line 49b: ST circuit breaker 49t: ST transformer 49m:ST power meter 50,50a,50b,50c: Liquefaction equipment 51: Bleed line 52: Bleed air volume control valve 53: Liquid air tank 54, 54a, 54b: Return air lines 55, 55a: Liquid air line 56: Liquid air pump 57: Return amount control valve 58, 58a, 58aa, 58b: Evaporative air lines 60,60a,60c,60d: Liquefaction system 61: Primary cooler (second cooling heat exchanger) 62: Secondary cooler 62a: Primary cooler 62c: Secondary cooler (first heating heat exchanger) 63,63c: Cooling device 64: Boost compressor 65: Expansion turbine 66: Tertiary cooler 67: Quaternary cooler (first cooling heat exchanger) 68m: High-pressure compressed air main line 68b: High-pressure compressed air branch line 68v: High compression air control valve 69m: Low temperature and low pressure air main line 69b: Low temperature and low pressure air branch line 70: Liquefied gas tank 71:First cooling heat exchanger 72: Liquefied gas line 72p: liquefied gas pump 72v: liquefied gas control valve 74: Gas-liquid mixing line 75: Expansion valve 77: Gas-liquid separation tank 78: Liquid air supply line 79: Liquid air supply control valve 80,80a,80b,80c: Heating system 81:First heating device 82: Gas-liquid tank 62c: Primary heater (first heating heat exchanger) 67: Primary heater (first heating heat exchanger) 83: Liquid air line for heating 84: Liquid air pump for heating 85: Liquid air control valve for heating 86: Evaporative air return line 88:Second heating device 89: Heat storage tank 91:Secondary heater (secondary heating heat exchanger) 92: Heat storage material supply line 92p: Heat storage material supply machine 93: High temperature heat storage material line 93v: Heat storage material control valve 94: Low temperature heat storage material line 95:Third heating device 96: Tertiary heater (third heating heat exchanger) 97: Branch steam line 97v: Branch steam control valve 100: Control device 101: Fuel controller 102:IGV controller 103: Liquefaction controller 110: Argon separator 111: Argon recovery tank PS:Power system CA: Compressed air HCA: High Compressed Air LLA: Low temperature low pressure air A: Air RA: Return air LA: Liquid air VA: Vaporized air HG: Heat storage material Ar: rotor axis Da: Axial direction Dau: Axis upstream side Dad: Downstream of axis

Claims

1. a gas turbine including a compressor capable of compressing air, a combustor capable of burning fuel in the compressed air compressed by the compressor to generate combustion gas, and a turbine capable of being driven by the combustion gas; A liquefaction facility capable of liquefying gaseous air; A liquefaction controller for controlling the liquefaction equipment; Equipped with The compressor includes a compressor rotor rotatable about an axis, a compressor casing covering an outer periphery of the compressor rotor, a plurality of stator vanes provided on an inner periphery of the compressor casing, and an intake air amount regulator capable of adjusting an intake air amount, which is a flow rate of air flowing into the compressor casing, by opening and closing the intake air amount regulator, The liquefaction facility comprises: an extraction line capable of extracting a portion of the compressed air from the compressor; a liquefaction system capable of liquefying the compressed air flowing through the extraction line; an extraction amount control valve capable of adjusting a flow rate of the compressed air flowing through the extraction line; a liquid air tank capable of storing liquid air, which is the compressed air liquefied in the liquefaction system; a return air line capable of guiding the liquid air in the liquid air tank or return air, which is vaporized air obtained by vaporizing the liquid air, to a flow path through which air or compressed air flows in the gas turbine, or to a high-temperature component that comes into contact with the combustion gas among components constituting the gas turbine; a return amount adjustment valve capable of adjusting a flow rate of the return air flowing through the return air line; having the liquefaction controller opens the extraction air amount control valve to guide the compressed air to the liquefaction system when the opening of the intake air amount regulator is a first opening or a parameter correlated with the opening has a value corresponding to the first opening, and opens the return amount control valve to guide the return air to the gas turbine when the opening of the intake air amount regulator is a second opening which is larger than the first opening or the parameter has a value corresponding to the second opening, the first opening degree is an opening degree when an amount of intake air flowing into the compressor casing is made smaller than an amount of intake air when an output of the gas turbine is a rated output. Gas turbine plant.

2. 2. The gas turbine plant according to claim 1, The first opening degree is a minimum opening degree that can minimize the amount of intake air flowing into the compressor casing. Gas turbine plant.

3. The gas turbine plant according to claim 1 or 2, The second opening degree is a maximum opening degree that can maximize the amount of intake air flowing into the compressor casing. Gas turbine plant.

4. The gas turbine plant according to claim 1 or 2, the liquefaction system comprising a cooling device capable of cooling the compressed air from the extraction line; The cooling device includes: a boost compressor capable of further compressing the compressed air from the bleed line to produce highly compressed air; an expansion turbine capable of adiabatically expanding a portion of the highly compressed air to generate low-temperature, low-pressure air; a first cooling heat exchanger capable of exchanging heat between another portion of the highly compressed air and the low-temperature low-pressure air to cool the highly compressed air; having Gas turbine plant.

5. The gas turbine plant according to claim 1 or 2, the liquefaction system comprising a cooling device capable of cooling the compressed air from the extraction line; The cooling device includes: A liquefied gas tank capable of storing liquefied gas; a first cooling heat exchanger capable of exchanging heat between the compressed air flowing through the extraction line and the liquefied gas to cool the compressed air; having Gas turbine plant.

6. The gas turbine plant according to claim 4, The liquefaction facility includes a heating system for heating the liquid air from the liquid air tank. Gas turbine plant.

7. 7. The gas turbine plant according to claim 6, The heating system includes a first heating device capable of heating the liquid air from the liquid air tank to generate vaporized air from the liquid air. Gas turbine plant.

8. The gas turbine plant according to claim 7, The first heating device is a gas-liquid tank capable of storing the liquid air and the vaporized air; a first heating heat exchanger capable of exchanging heat between the liquid air in the gas-liquid tank and the compressed air, heating the liquid air and returning the liquid air to the gas-liquid tank as the vaporized air, while cooling the compressed air; The liquefaction system has the first heating heat exchanger as a cooling heat exchanger capable of cooling the compressed air. Gas turbine plant.

9. The gas turbine plant according to claim 4, the liquefaction facility includes a heating system for heating the liquid air from the liquid air tank; the heating system includes a first heating device capable of heating the liquid air from the liquid air tank to generate vaporized air by vaporizing the liquid air; The first heating device is a gas-liquid tank capable of storing the liquid air and the vaporized air; a first heating heat exchanger capable of exchanging heat between the liquid air from the gas-liquid tank and the other part of the highly compressed air from the boost compressor, heating the liquid air and returning the liquid air to the gas-liquid tank as the vaporized air, while cooling the other part of the highly compressed air; the liquefaction system has the first heating heat exchanger as the first cooling heat exchanger, The first heating heat exchanger as the first cooling heat exchanger is capable of exchanging heat between the liquid air from the gas-liquid tank and the low-temperature low-pressure air from the expansion turbine, and the other part of the highly compressed air from the boost compressor. Gas turbine plant.

10. The gas turbine plant according to claim 7, The heating system includes a second heating device capable of heating the vaporized air from the first heating device. Gas turbine plant.

11. The gas turbine plant according to claim 10, The liquefaction system has a second cooling heat exchanger capable of heating the heat storage material by exchanging heat between the compressed air before reaching the cooling device and the heat storage material, and also capable of cooling the compressed air; The second heating device is a heat storage tank capable of storing the heat storage material heated by the second cooling heat exchanger; a second heating heat exchanger capable of exchanging heat between the heat storage material from the heat storage tank and the vaporized air from the first heating device to heat the vaporized air while cooling the heat storage material; having The second cooling heat exchanger is capable of exchanging heat between the compressed air before reaching the cooling device and the heat storage material cooled by the second heating heat exchanger. Gas turbine plant.

12. The gas turbine plant according to claim 11, the heating system includes a third heating device capable of heating the vaporized air from the second heating device, The return air line is capable of guiding the vaporized air heated by the third heating device as the return air to a flow path in the gas turbine through which the compressed air flows. Gas turbine plant.

13. 13. The gas turbine plant according to claim 12, a heat recovery boiler capable of generating steam by utilizing heat of exhaust gas, which is a combustion gas exhausted from the gas turbine; The third heating device has a third heating heat exchanger capable of heating the vaporized air by heat exchange between the vaporized air from the second heating device and the steam from the heat recovery boiler. Gas turbine plant.

14. In the gas turbine plant according to any one of claims 1 and 2, The liquefaction system has an argon separator capable of cryogenically separating argon in the compressed air during the liquefaction process of the compressed air in the liquefaction system. Gas turbine plant.

15. The gas turbine plant according to claim 1 or 2, The return air line may direct the return air into a flow path of the compressed air through the gas turbine. Gas turbine plant.

16. The gas turbine plant according to claim 1 or 2, The return air line is capable of directing the return air into an air flow path in the compressor casing. Gas turbine plant.

17. 17. The gas turbine plant according to claim 16, The return air line is capable of guiding the return air to a flow path portion in the air flow path in the compressor casing through which air flows before the intake air amount is adjusted by the intake air amount adjuster. Gas turbine plant.

18. 17. The gas turbine plant according to claim 16, At least one of the plurality of stator vanes of the compressor has an air passage formed therein that passes through the stator vane and opens at a surface of the stator vane, the return air line may direct the return air into the air passage of the vane. Gas turbine plant.

19. 19. The gas turbine plant according to claim 18, the return air line is capable of directing the liquid air as the return air into the air passage of the vane. Gas turbine plant.

20. The gas turbine plant according to claim 1 or 2, the high temperature component is formed with a cooling air passageway passing through the high temperature component and opening at a surface of the high temperature component in contact with the combustion gas; the return air line is capable of directing the return air to the cooling air passage of the hot component; Gas turbine plant.

21. A gas turbine is provided. The gas turbine includes a compressor capable of compressing air, a combustor capable of burning fuel in compressed air compressed by the compressor to generate combustion gas, and a turbine capable of being driven by the combustion gas, The compressor includes a compressor rotor rotatable about an axis, a compressor casing covering an outer periphery of the compressor rotor, a plurality of stator vanes provided on an inner periphery of the compressor casing, and an intake air amount regulator capable of adjusting an intake air amount, which is a flow rate of air flowing into the compressor casing, by opening and closing the intake air amount regulator. A method for operating a gas turbine plant, comprising: a bleeding step of bleeding a portion of the compressed air from the compressor; a liquefaction step of liquefying the compressed air extracted in the extraction step to generate liquid air; a return step of guiding the liquid air or the return air obtained by vaporizing the liquid air to a flow path through which air or compressed air flows in the gas turbine, or to a high-temperature part that comes into contact with the combustion gas in a part constituting the gas turbine; Including, The air extraction process and the liquefaction process are carried out when the opening degree of the intake air regulator is a first opening degree or when a parameter having a correlation with the opening degree has a value corresponding to the first opening degree; When the opening degree of the intake air regulator is a second opening degree larger than the first opening degree or when the parameter has a value corresponding to the second opening degree, the returning step is executed; the first opening degree is an opening degree when an amount of intake air flowing into the compressor casing is made smaller than an amount of intake air when an output of the gas turbine is a rated output. A method for operating a gas turbine plant.

22. 22. The method for operating a gas turbine plant according to claim 21, The first opening degree is a minimum opening degree that can minimize the amount of intake air flowing into the compressor casing. A method for operating a gas turbine plant.

23. The method for operating a gas turbine plant according to claim 21 or 22, The second opening degree is a maximum opening degree that can maximize the amount of intake air flowing into the compressor casing. A method for operating a gas turbine plant.

24. The method for operating a gas turbine plant according to claim 21 or 22, The liquefaction step includes an argon separation step of cryogenically separating argon in the compressed air during the liquefaction of the compressed air. A method for operating a gas turbine plant.

25. A gas turbine is provided. The gas turbine includes a compressor capable of compressing air, a combustor capable of burning fuel in compressed air compressed by the compressor to generate combustion gas, and a turbine capable of being driven by the combustion gas, The compressor includes a compressor rotor rotatable about an axis, a compressor casing covering an outer periphery of the compressor rotor, a plurality of stator vanes provided on an inner periphery of the compressor casing, and an intake air amount regulator capable of adjusting an intake air amount, which is a flow rate of air flowing into the compressor casing, by opening and closing the intake air amount regulator. A method for modifying a gas turbine plant, comprising: Adding a liquefaction device capable of liquefying gaseous air and a liquefaction controller for controlling the liquefaction device, The liquefaction equipment added in the process includes: an extraction line capable of extracting a portion of the compressed air from the compressor; a liquefaction system capable of liquefying the compressed air flowing through the extraction line; a liquid air tank capable of storing liquid air, which is the compressed air liquefied in the liquefaction system; an extraction amount control valve capable of adjusting a flow rate of the compressed air flowing through the extraction line; a return air line capable of guiding the liquid air in the liquid air tank or return air, which is vaporized air obtained by vaporizing the liquid air, to a flow path through which air or compressed air flows in the gas turbine, or to a high-temperature component that comes into contact with the combustion gas among components constituting the gas turbine; a return amount adjustment valve capable of adjusting a flow rate of the return air flowing through the return air line; having the liquefaction controller added in the step opens the extraction air amount control valve to guide the compressed air to the liquefaction system when the opening of the intake air amount regulator is a first opening or a parameter correlated with the opening has a value corresponding to the first opening, and opens the return amount control valve to guide the return air to the gas turbine when the opening of the intake air amount regulator is a second opening which is larger than the first opening or the parameter has a value corresponding to the second opening, the first opening degree is an opening degree when an amount of intake air flowing into the compressor casing is made smaller than an amount of intake air when an output of the gas turbine is a rated output. A method for modifying a gas turbine plant.

26. The method for modifying a gas turbine plant according to claim 25, The liquefaction system has an argon separator capable of cryogenically separating argon in the compressed air during the liquefaction process of the compressed air in the liquefaction system. A method for modifying a gas turbine plant.

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