JP2014047657A - Moisture utilizing gas turbine system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a moisture utilizing gas turbine system in which efficiency is improved as further as possible, the moisture utilizing gas turbine system being configured to extract compressed air from a compressor.SOLUTION: In a moisture utilizing gas turbine system for extracting compressed air from a compressor of a gas turbine, heat retained in the extracted compressed air is collected. For example, a heat exchanger is provided which heats gas turbine exhaust gas after passing through a water collector for collecting moisture in the gas turbine exhaust gas with compressed air partially extracted from the compressor. The compressed air cooled by the heat exchanger is expanded by an expansion turbine to collect power and air the temperature of which is lowered by expansion is utilized for cold supply.

Description

  The present invention relates to a moisture-based gas turbine system that improves efficiency by humidifying combustion air of a gas turbine, and in particular, supplies steam to the combustion air and compresses the air compressed by a compressor outside the gas turbine. The present invention relates to a moisture-based gas turbine system that performs air extraction.

  As a moisture-utilizing gas turbine system, steam is injected into the combustor of the gas turbine, the flow rate of the combustion gas flowing into the turbine is increased, and the specific heat of the combustion gas is increased to increase the output of the turbine. There are those described in Document 1 and Patent Document 2.

  Patent Document 1 includes an injection steam line that guides and injects a part of steam generated by an exhaust heat boiler to a combustor, and an air extraction line that extracts compressed air by a compressor. It has been proposed to produce a large amount of compressed air without using a turbine compressor while supplying process steam by a thermal boiler at the same level or higher. In Patent Document 1, the amount of compressed air that is substantially proportional to the amount of steam injected into the combustor is extracted, and the compressor outlet pressure is kept substantially constant, thereby increasing the turbine output by increasing the amount of injected steam. However, it has been proposed to prevent compressor surging. Furthermore, Patent Document 1 includes a heat exchanger that indirectly exchanges heat between an injection steam line and an air extraction line, and is configured to heat the injection steam with high-temperature extraction air, thereby overheating the exhaust heat boiler. It has been proposed to overheat the jet steam without providing a vessel, to reduce the size of the apparatus and to increase the overall thermal efficiency. According to Patent Document 1, all surplus steam other than process steam is injected into the combustor and is recovered through the turbine to a low temperature (for example, around 100 ° C.) with a heat exhaust boiler. It can be reduced.

  Patent Document 2 also includes an injection steam line that guides and injects water vapor into a combustor, and an extraction air cooling line that extracts compressed air from the compressor, and a compressed air amount that is substantially proportional to the amount of injection steam to the combustor. It has been proposed to keep the compressor outlet pressure substantially constant and to prevent the compressor from surging while increasing the turbine output by increasing the amount of injected steam. Further, in Patent Document 2, the extraction air is cooled and expanded in the extraction air cooling line to generate low-temperature air, and the generated low-temperature air is supplied to the intake air mixing cooler and directly mixed with the intake air of the compressor. It has been proposed to reduce the compression power in the compressor, increase the combustion amount in the combustor while maintaining the turbine inlet temperature, and increase the turbine output by reducing the intake air temperature. Also in Patent Document 2, all of the supplied surplus steam is injected into the combustor, and heat is recovered to a low temperature (for example, around 100 ° C.) through a turbine, for example, with an exhaust heat boiler or the like. It can be reduced.

  In Patent Literature 3, as a moisture-utilizing gas turbine system, the energy recovered from the exhaust heat of the gas turbine is used to humidify the compressed air of the gas turbine with a humidifier to increase the mass flow rate and enthalpy of the combustion air, A high-humidity air-utilizing gas turbine is disclosed in which a turbine is driven by a high-temperature combustion gas obtained by combusting the high-humidity air and fuel in a combustor to improve gas turbine output and power generation efficiency. Moreover, in patent document 3, in order to collect | recover and reuse the moisture contained in the exhaust gas of a gas turbine, the water collection | recovery apparatus is provided. This water recovery device is configured to spray droplets in exhaust gas and collect moisture by condensing moisture in the exhaust gas by direct gas-liquid contact. Moreover, in patent document 3, in order to prevent the exhaust gas which passed the water collection | recovery apparatus from being discharged | emitted as white smoke from a chimney, it describes that it heats with an exhaust gas reheating apparatus.

JP-A-9-203327 Japanese Patent Laid-Open No. 11-257098 JP 2007-16640 A

  In patent document 1, the heat exchanger which indirectly heat-exchanges with an injection steam line and an air extraction line is provided, and injection steam is heated with high temperature extraction air. As a specific example, the example of Patent Document 1 describes that after heating high-temperature compressed air of about 380 ° C. from a compressor, about 200 ° C. saturated steam generated by an exhaust heat boiler is heated. . The compressed air after heating the steam still retains 250 ° C. thermal energy. However, Patent Document 1 aims to cool compressed air in order to use compressed air externally, and has been studied only from the viewpoint of cooling compressed air. The thermal energy of 250 ° C. possessed by compressed air is considered. There is no room for improvement in efficiency, leaving room for improvement in efficiency.

  In Patent Document 2, the extraction air is cooled and expanded in the extraction air cooling line to generate low-temperature air. As a specific example, the example of Patent Document 2 describes that compressed air is cooled to around 50 ° C. with cooling water and then expanded by an expansion turbine to generate low temperature air around −60 ° C. In Patent Document 2, the purpose is to obtain low-temperature air from the extracted compressed air, which has been studied only from the viewpoint of generating low-temperature air, and the use of the heat of the compressed air extracted from the compressor is completely considered. There is still room for efficiency improvement.

  In patent document 3, it is not comprised so that the air compressed with the compressor may be extracted outside, and the utilization of the heat of the compressed air extracted from the compressor is not taken into consideration at all.

  An object of the present invention is to provide a moisture-use gas turbine system that improves efficiency as much as possible in a moisture-use gas turbine system that extracts compressed air from a compressor.

  The present invention is characterized in that in a moisture-based gas turbine system that extracts compressed air from a compressor of a gas turbine, the heat of the extracted compressed air is recovered.

  It is desirable to recover the power by expanding the compressed air after recovering heat with an expansion turbine.

  ADVANTAGE OF THE INVENTION According to this invention, efficiency can be improved as much as possible in the moisture utilization gas turbine system which extracts a part of compressed air from a compressor.

  Problems, configurations, and effects other than those described above will be clarified by the following description of embodiments.

1 is a schematic system diagram showing a moisture-use gas turbine system that is an embodiment of the present invention. The schematic system diagram which shows the moisture utilization gas turbine system which is the other Example of this invention.

  A moisture-use gas turbine system according to an embodiment of the present invention will be described below with reference to the drawings.

  First, the outline of the present embodiment will be described. This embodiment is a moisture-use gas turbine system in which steam is supplied to a combustor of a gas turbine to increase the output of the turbine. In such a moisture-utilizing gas turbine system, compressed air is extracted from the compressor for flow rate matching between the compressor and the turbine.

  The present embodiment improves the efficiency as much as possible in such a moisture-utilizing gas turbine system by recovering the heat held by the compressed air. Conventionally, in such a moisture-utilizing gas turbine system, as described in Patent Document 1 and Patent Document 2, a water recovery device that recovers moisture in the gas turbine exhaust is not provided. In this embodiment, a moisture recovery gas turbine system in which steam is supplied to a gas turbine combustor to increase the output of the turbine is newly provided with a water recovery device to heat the exhaust gas whose temperature has been reduced during water recovery. In this way, compressed air is used as a heating medium (heating-side fluid) of the exhaust gas reheater that suppresses the generation of white smoke, and the heat held by the compressed air is recovered.

  Further, in this embodiment, a heat exchanger for heating the fuel supplied to the combustor is provided, and the heat held by the compressed air is recovered by using the compressed air as a heating medium (heating side fluid) of the heat exchanger. ing.

  In the present embodiment, the compressed air after the heat is recovered by the exhaust gas reheater is expanded by the expansion turbine to recover the power. In this embodiment, a tri-generation system capable of supplying three types of electric power, steam, and cold is constructed by using the air that has been expanded and lowered in temperature as a cold heat source.

  Hereinafter, it demonstrates concretely using drawing. FIG. 1 is a schematic system diagram showing the configuration of a moisture-utilizing gas turbine system according to an embodiment of the present invention. The main components of the gas turbine main body are a compressor 2 that compresses and discharges air, a combustor 4 that mixes and burns compressed air and fuel, and a turbine 1 that is driven by combustion gas generated by the combustor. . The shaft 5 that connects the compressor 2 and the turbine 1 is connected to a generator 19 via a reduction gear (not shown), so that the generated power can be transmitted to the system.

  The compressed air discharged from the compressor 2 is guided to the combustor 4 via a flow path 53 in the gas turbine casing. In the combustor 4, combustion gas is generated by mixing with compressed air, fuel supplied from the pipe 43, and superheated steam supplied from the pipe 41. The combustion gas drives the turbine 1 and is exhausted from the turbine as exhaust gas 13. The exhaust heat recovery boiler 26, the water recovery device 17, and the exhaust gas reheater 88 are connected to the flow path of the exhaust gas 13 in order from the upstream side, and the exhaust gas is finally released from the stack 54 into the atmosphere.

  The exhaust heat recovery boiler 26 includes an economizer 23, an evaporator 24, and a superheater 25. The steam drum of the evaporator 24 has a structure capable of supplying saturated steam to the outside by a pipe 34 and a valve 74. ing.

  In the present embodiment, the humidifier that adds moisture to the air compressed by the compressor includes the exhaust heat recovery boiler 26, the pipe 41, and the valve 73. That is, the superheated steam generated by the superheater 25 of the exhaust heat recovery boiler 26 can be supplied to the combustor 4 via the pipe 41 and the valve 73. In the present specification, the description of “supplying steam to the combustor 4” not only indicates that steam is supplied into the combustor 4 but also combustion in which compressed air introduced into the combustor 4 flows down. It also includes supplying steam to the air flow path (flow path 53).

  The water recovery device 17 pressurizes the water held in the recovered water container 18 by the pump 92 installed in the pipe 31, cools it with the cooler 85, and then is installed inside the water recovery apparatus 17 by the pipe 32. It is configured to supply to the spray nozzle 71. The cooler 85 is an air-cooled cooler that cools water by introducing the air 93 by the fan 27. The water held in the recovered water container 18 is piped so as to be supplied to the economizer 23 of the exhaust heat recovery boiler 26 by a pump 91 installed in the pipe 33. Further, the recovered water container 18 of the water recovery device 17 is provided with a pipe 52 so that makeup water can be supplied from the outside.

  A component that is a feature of the present embodiment is an extraction system that extracts a part of the compressed air discharged from the compressor 2 to the outside of the casing of the gas turbine through a pipe 42. In order, a valve 66, a heat exchanger 55, a pipe 44, an exhaust gas reheater 88, a pipe 45, an expansion turbine 28, a pipe 46, a heat exchanger 56, and a pipe 47 are connected. The heat exchanger 55 is installed for the purpose of heating the fuel 95, and the exhaust gas reheater 88 heats the exhaust gas cooled to a low temperature by the water recovery device 17 to suppress the generation of white smoke in the atmosphere. It is installed for the purpose. The expansion turbine 28 is connected to the generator 20 and can convert pressure energy held by the compressed air into electric power. The heat exchanger 56 is configured to be able to introduce a heat medium such as propylene glycol from the pipe 48 and supply the heat medium cooled from the pipe 49 to the outside.

  Next, the operation of the moisture-use gas turbine system according to this embodiment will be described with reference to FIG. The air sucked from the intake duct 3 of the gas turbine is compressed by the compressor 2 and is discharged from the compressor 2 as high-temperature compressed air. Most of the discharged compressed air is guided to the combustor 4 via the flow path 53 in the gas turbine casing. In the combustor 4, the fuel 95, superheated steam supplied from the piping 41, and compressed air are mixed and burned to generate high-temperature combustion gas. This high-temperature combustion gas is supplied to the turbine 1, expands inside the turbine 1, and heat energy is converted into motive energy. This motive energy is consumed for driving the compressor 2 connected to the same shaft 5, and is converted into electric energy and taken out by the generator 19.

  In this moisture-utilizing gas turbine, the steam generated by exhaust heat recovery is added to the air to be burned as moisture, so the flow rate of the combustion gas supplied to the turbine is higher than that of a normal simple cycle gas turbine. Become. In this case, since the pressure ratio of the gas turbine increases and surging of the compressor 2 is likely to occur, the opening degree of the valve 66 of the pipe 42 is set so that the air pressure at the outlet of the compressor 2 is less than the allowable value. To adjust the flow rate of the compressed air extracted from the extraction system.

  When the mass of the added water vapor increases, the mass of compressed air that needs to be extracted also increases, but the thermal energy per unit mass of water vapor is larger than that of compressed air, so that it is higher than that of a normal gas turbine. More energy can be extracted, improving system thermal efficiency.

  The exhaust gas 13 discharged through the expansion process in the turbine 1 is guided to the exhaust heat recovery boiler 26, and the water supplied from the pipe 33 is sequentially heated by the economizer 23, the evaporator 24, and the superheater 25 to generate water vapor. . Saturated steam can be extracted from the steam drum of the evaporator 24 through the pipe 34, and can be used for process steam and heating as needed. The superheated steam generated by the superheater 25 is supplied to the above-described combustor 4 and contributes to the output and efficiency improvement of the gas turbine.

  The exhaust gas discharged from the exhaust heat recovery boiler 26 is guided to the water recovery device 17. In the water recovery device 17, the recovered water stored in the recovered water container 18 in the lower space is supplied to the cooler 85 by the pump 92 of the pipe 31. It is cooled to 35 ° C. and supplied to the spray nozzle 71. The spray water sprayed from the spray nozzle 71 and the exhaust gas 13 come into direct gas-liquid contact, and the moisture contained in the exhaust gas 13 is condensed and recovered in the recovery water container 18. The exhaust gas discharged from the water recovery device 17 is a wet gas (for example, a wet gas of 40 ° C. or lower) cooled by spray water, in order to suppress dew condensation inside the stack 54 and generation of white smoke in the atmosphere. Then, it is heated to, for example, 80 ° C. by the exhaust gas reheater 88 and then released into the atmosphere by the stack 54. A part of the recovered water in the recovered water container 18 is supplied to the economizer 23 of the exhaust heat recovery boiler 26 by the pump 91 of the pipe 33. The water level of the recovered water container 18 of the water recovery device 17 varies depending on the balance between the amount of water recovered by the condensation of the exhaust gas 13 and the amount of water supplied from the pipe 33 to the exhaust heat recovery boiler 26. Therefore, when the recovery amount is larger than the supply amount to the boiler, excess water is discharged by a drainage mechanism (not shown), and when the recovery amount is smaller than the supply amount to the boiler, makeup water is supplied from the pipe 52. The water level of the recovered water container 18 is maintained.

  Next, the operation of the extraction system from the compressor, which is a characteristic system of the present embodiment, will be described. A control device (not shown) automatically controls the opening degree of the valve 66 of the pipe 42 so that the air pressure at the outlet of the compressor is less than or equal to an allowable value from the viewpoint of preventing the compressor from surging. Bleed to the outside. This flow rate depends on the surging characteristics of the compressor, but is typically about 5 to 20% of the suction flow rate of the compressor. In a situation where it is desired to use more steam generated in the evaporator 24 for process steam and heating, the flow rate of superheated steam that can be injected into the combustor 4 decreases, and the flow rate of compressed air extracted from the extraction system decreases. On the other hand, in a situation where demand for process steam and steam for heating is low, the flow rate of superheated steam injected into the combustor 4 is increased, and the flow rate of compressed air extracted from the extraction system by automatic control is increased. By this bleed operation from the compressor, the outlet pressure of the compressor is automatically maintained within the range of the reference value, and the compressor 2 can be operated in a stable state.

  In the heat exchanger 55, the fuel 95 is heated to about 300 ° C. by the high-temperature compressed air of about 400 ° C., and the temperature of the compressed air is reduced to about 320 ° C. By heating this fuel, the flow rate of the fuel 95 necessary for generating combustion gas at a desired temperature in the combustor 4 is reduced by about 3%, and the system thermal efficiency is improved by about 3%. The compressed air having a temperature of about 320 ° C. via the heat exchanger 55 is supplied to the exhaust gas reheater 88 which is a heat exchanger, and the compressed air is heated to about 80 ° C. by heating the low temperature exhaust gas of about 40 ° C. The temperature drops to about 100 ° C. Due to this heating, the degree of superheat of the exhaust gas becomes 40 ° C. or higher, and therefore, dew condensation is suppressed inside the stack 54. Further, even after being released from the stack 54 into the atmosphere, the generation of white smoke can be suppressed and the landscape of the power generation facility can be maintained.

  The compressed air whose temperature has been lowered to about 100 ° C. by the exhaust gas reheater 88 is introduced into the expansion turbine 28. When the compressed air is expanded to almost atmospheric pressure by the expansion turbine 28, the temperature is reduced to about -70 ° C due to the external work. The low-temperature air whose temperature has decreased to about −70 ° C. is guided to the heat exchanger 56 through the pipe 46 and used as a cold heat source. At this time, the power generated by the expansion turbine is converted into electric power by the generator 20 and used. This power is about 6% of the output of the gas turbine, and has the effect of improving the overall thermal efficiency of the system by about 6%.

  The heat exchanger 56 is supplied with about 15 ° C. propylene glycol returned from the customer in the cold supply application through a pipe 48. Propylene glycol, which is the heat medium, is indirectly heat-exchanged with low-temperature air of about -70 ° C in the heat transfer pipe inside the heat exchanger 56, cooled to about 5 ° C, and supplied from the pipe 49 to the external cold energy demand destination. Is done. The amount of heat of this cold is about 3% of the output of the gas turbine, and has the effect of improving the overall thermal efficiency of the system by about 3%.

  When there is no demand for cold heat, the supply of a heat medium such as propylene glycol is stopped, so that low-temperature air is released as it is from the pipe 47. Connected to the duct portion, the low-temperature air is heated by the exhaust gas reheater 88 and then released to the atmosphere. The flow rate of air passing through the pipe 47 is about 20% at the maximum of the flow rate of the exhaust gas 13. Even when this is mixed, the gas temperature at the outlet of the exhaust gas reheater 88 is heated to 60 ° C. or higher. There is no hindrance to release.

  A unique feature of the present embodiment is that the high-temperature bleed air of about 400 ° C. from the compressor 2 is subjected to heat exchange with the low-temperature air of about 40 ° C. at the outlet of the water recovery device 17. Until the temperature drops from about 400 ° C. to about 100 ° C., it is possible to recover heat effectively without discarding heat to the outside. The total system efficiency improvement effect of the present embodiment described above is totaled to be about 12%, and the total thermal efficiency of the system is conspicuous compared to the case where heat recovery, power recovery, etc. are not performed from extraction of compressed air. Can be improved.

  In this embodiment, for supplying cold heat, the heat exchanger 56 is provided and propylene glycol is used as a heat medium. However, a heat medium other than propylene glycol may be used. By providing the heat exchanger 56 as in the present embodiment, it is possible to transport cold using a suitable heat medium according to the purpose of use.

  In addition, depending on the use of cold heat, it is naturally possible to supply low-temperature air of about −70 ° C. as it is to a cold-heat customer. However, in the case of air, the amount of retained heat per volume is smaller than that of a heat medium such as propylene glycol. Therefore, there is a tendency that the pressure loss necessary for transporting cold heat tends to increase, and it is desirable that the cold heat demand destination is in a short distance from the gas turbine system of the present embodiment.

  Moreover, although the spray type was illustrated as the water collection | recovery apparatus 17 in the present Example, the same operation | movement is possible not with a spray type but with a filling type and a heat exchanger tube type. The spray type has the feature that the pressure loss on the exhaust gas side can be reduced, but in order to improve the condensation performance of moisture, it is required to make the flow rate distribution of exhaust gas and spray droplets uniform. In the packing type, it is relatively easy to make the flow distribution on the exhaust gas side uniform, but the pressure loss on the exhaust gas side tends to increase. The heat transfer tube type has the feature that moisture can be recovered from the exhaust gas without using any cooling water by supplying cooling air directly to the heat transfer tube, but it is necessary to increase the heat transfer area. The exhaust gas flow path portion of the water recovery device tends to be enlarged.

  In this embodiment, the expansion turbine 28 is provided on the downstream side of the exhaust gas reheater 88 as the expansion means for expanding the compressed air. However, the expansion turbine 28 is replaced with an expansion valve or the like, and only cold heat is used. It is good also as composition to do.

  Furthermore, in this embodiment, the case where the present invention is applied to a moisture-based gas turbine system in which humidification of compressed air is performed by injecting steam generated in the exhaust heat recovery boiler 26 into a combustor has been described. The humidification to the compressed air can be similarly applied to a high-humidity air-utilizing gas turbine facility such as described in Patent Document 3 using a humidification tower and an economizer. For example, in the high-humidity air-utilizing gas turbine facility of Patent Document 3, for the flow rate matching between the compressor and the turbine, a configuration for extracting (releasing) compressed air from the compressor is added, and the exhaust gas discharged from the water recovery device As the heat medium of the exhaust gas reheating device for reheating the gas, the extracted compressed air is used instead of the circulating water supplied to the economizer. By configuring in this way, even if the exhaust gas reheating device is installed, the circulating water supplied to the economizer is not used, so that the temperature of the water supplied to the economizer can be avoided from decreasing, and as a result, the economizer The energy of hot water supplied to the humidification tower is reduced, the amount of exhaust heat recovered in the entire system is reduced, and it is possible to avoid a reduction in efficiency.

  A moisture-use gas turbine system according to another embodiment of the present invention will be described with reference to FIG.

  The moisture-use gas turbine system of this embodiment has the same basic configuration and operation as the moisture-use gas turbine system of the previous embodiment shown in FIG. Therefore, the description of the configuration common to the first embodiment is omitted, and only different portions will be described below.

  In this embodiment, the heat exchanger 55 according to the embodiment described with reference to FIG. 1 is not provided and the fuel 95 is not heated by the high-temperature air extracted from the compressor 2 in this embodiment. In addition, a fuel compressor 29 and an electric motor / generator 22 are connected to the expansion turbine 28 via the shaft 6 instead of the generator 20.

  Hereinafter, the specific operation of this embodiment will be described with reference to FIG.

  Also in the present embodiment, as in the first embodiment, from the viewpoint of preventing the surging of the compressor, the opening degree of the valve 66 of the pipe 42 is automatically controlled so that the air pressure at the compressor outlet is equal to or less than the allowable value. Then, the compressed air having a necessary flow rate is extracted outside. The high temperature compressed air of about 400 ° C. is supplied to the exhaust gas reheater 88, and the temperature of the compressed air is lowered to about 100 ° C. by heating the low temperature exhaust gas of about 40 ° C. to about 90 ° C. By this heating, the degree of superheat of the exhaust gas becomes 50 ° C. or higher, and it is possible to suppress the formation of dew condensation inside the stack 54, and no white smoke is generated after being released into the atmosphere from the stack 54. There is an effect to maintain.

  The compressed air whose temperature has been lowered to about 100 ° C. by the exhaust gas reheater 88 is introduced into the expansion turbine 28. When the expansion turbine 28 expands to approximately atmospheric pressure, the temperature is reduced to about −70 ° C. due to the outside work, and is led to the heat exchanger 56. In this embodiment, the power generated in the expansion turbine 28 at this time is used as power for driving the fuel compressor 29. Depending on the pressure ratio of the fuel compressor and the amount of heat of the fuel, if the power required for driving the fuel compressor 29 is smaller than the power generated by the expansion turbine 28, the motor / generator 22 is operated as a generator. The surplus power is converted into electric power for use. On the contrary, when the power required for driving the fuel compressor 29 is larger than the power generated by the expansion turbine 28, power is supplied to the electric motor / generator 22 to drive the fuel compressor 29. generate.

  In this embodiment, since the fuel 95 is compressed by the fuel compressor 29, the fuel 95 is supplied to the combustor 4 in a state where the temperature has risen. The point that the low-temperature air at the outlet of the expansion turbine 28 is used for cold supply is the same as in the first embodiment.

  A unique feature of this embodiment is that the power generated by the expansion turbine 28 is used to directly drive the fuel compressor 29. The power generated by the expansion turbine 28 is used after being converted into electric power. Compared to the case, the loss is not caused by the conversion between power and power.

  As described above, according to the present embodiment, the overall thermal efficiency of the system can be remarkably improved as compared with the case where heat recovery, power recovery, and the like are not performed from extraction of compressed air.

  In the present embodiment, the modification described in the first embodiment can be similarly applied except when an expansion valve is used instead of the expansion turbine.

  In addition, this invention is not limited to an above-described Example, Various modifications are included. For example, the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described. Further, a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment. Moreover, it is possible to add, delete, and replace other configurations for a part of the configuration of each embodiment.

1: turbine, 2: compressor, 3: intake duct, 4: combustor, 5, 6: shaft, 13: exhaust gas, 17: water recovery device, 18: recovered water container, 19, 20: generator, 22 : Motor / generator, 23: economizer, 24: evaporator, 25: superheater, 26: exhaust heat recovery boiler, 27: fan, 28: expansion turbine, 29: fuel compressor, 31, 32, 33, 34, 41, 42, 43, 44, 45, 46, 47, 48, 49, 52: piping, 53: flow path, 54: stack, 55, 56: heat exchanger, 66: valve, 71: spray nozzle, 73, 74: valve, 85: cooler, 88: exhaust gas reheater, 91, 92: pump, 93: air, 95: fuel.

Claims (10)

  A compressor that compresses air; a combustor that generates a combustion gas by mixing and burning moisture and fuel in the air compressed by the compressor; and a turbine that is driven by the combustion gas from the combustor. A water recovery device that recovers moisture from the exhaust gas of the turbine, and a heat exchanger that heats the gas turbine exhaust gas that has passed through the water recovery device, and is extracted from the compressor as a heating-side fluid of the heat exchanger A moisture-utilizing gas turbine system using compressed air. The moisture-use gas turbine system according to claim 1,
A moisture-utilizing gas turbine system comprising a heat exchanger for heating fuel supplied to the combustor, and using compressed air extracted from the compressor as a heating side fluid of the heat exchanger for heating the fuel . In the moisture utilization gas turbine system according to claim 1 or 2,
An expansion means for expanding compressed air that has passed through a heat exchanger for heating the gas turbine exhaust gas;
A moisture-use gas turbine system comprising a system for supplying low-temperature air expanded by the expansion means to a cold-use facility. The moisture-use gas turbine system according to claim 3,
The means for expanding the compressed air is an expansion turbine;
A moisture-use gas turbine system comprising a generator driven by the expansion turbine. The moisture-use gas turbine system according to claim 3,
The means for expanding the compressed air is an expansion turbine;
A moisture-use gas turbine system comprising a fuel compressor driven by the expansion turbine and compressing fuel supplied to the combustor. The moisture-use gas turbine system according to claim 3,
A heat exchanger for exchanging heat between the low-temperature air and the heat medium as the cold energy utilization facility,
A moisture-use gas turbine system comprising a system for supplying the heat medium, which has been cooled to a low temperature by a heat exchanger that exchanges heat between the low-temperature air and the heat medium, to another cold energy utilization facility.   A compressor that compresses air; a combustor that generates a combustion gas by mixing and burning moisture and fuel in the air compressed by the compressor; and a turbine that is driven by the combustion gas from the combustor. And a heat exchanger that heats the fuel supplied to the combustor, wherein the compressed gas extracted from the compressor is used as a heating-side fluid of the heat exchanger. The moisture-use gas turbine system according to claim 7,
Comprising expansion means for expanding compressed air that has passed through a heat exchanger for heating the fuel;
A moisture-use gas turbine system comprising a system for supplying low-temperature air expanded by the expansion means to a cold-use facility. The moisture-use gas turbine system according to claim 8,
The means for expanding the compressed air is an expansion turbine;
A moisture-use gas turbine system comprising a generator driven by the expansion turbine. The moisture-use gas turbine system according to claim 8,
A heat exchanger for exchanging heat between the low-temperature air and the heat medium as the cold energy utilization facility,
A moisture-use gas turbine system comprising a system for supplying the heat medium, which has been cooled to a low temperature by a heat exchanger that exchanges heat between the low-temperature air and the heat medium, to another cold energy utilization facility.

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