JP2001132473A - Gas turbine system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gas turbine system for increasing the power generation efficiency of a plant. SOLUTION: This system is provided with a first sprayer 21 for humidifying a first air 110 compressed and branched by a compressor 1, a heat exchanger 23 for heat exchanging the first air 110 humidified by the first sprayer 21 and a second air 130 branched by a branch 30 and a second sprayer 22 for humidifying the heat exchanged second air 131. A low temperature humidified air 132 is introduced to the gas turbine exhaust gas down streamside of a reproduced heat exchanger 3 and a high temperature humidified air 112 is introduced to the gas turbine exhaust gas upper streamside than the introduction point of the low temperature humidified air 132.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gas turbine system provided with a turbine operated by a combustion gas containing moisture, and more particularly to a gas turbine system which increases the moisture content of air supplied to a combustor to reduce the moisture content of the combustion gas. Gas turbine system with increased volume.

[0002]

2. Description of the Related Art As a prior art relating to a gas turbine system using humidified air, for example, Japanese Patent Publication No. 1-31012 and Japanese Patent Application Laid-Open No. 9-264158 disclose compressed air formed by a compressor and heat. The heated liquid-phase water used as a recovery medium is brought into contact with a humidification tower to obtain humidified air (a mixture of air / steam) and cooled liquid-phase water. The recovered liquid-phase water is used as a heat recovery medium to recover the heat of the turbine exhaust and cool the compressor intermediately. Further, the exchange tower (humidification tower) uses the exchange tower to convert the amount of liquid-phase water that has been transferred to the compressed air as steam into the exchange tower. A gas turbine cycle is disclosed that is used as a cooling medium downstream of the intercooler of the compressor with the resulting cooled liquid-phase water and replenishes into the liquid phase that is subjected to an exchange tower and heat recovery.

As a humidifying device for humidifying and reducing the temperature of air, Journal of Engineering for Gas Turbines and Pow
er Vol. 119 / 893-897 (1997), J. De Ruyck et al. obtained by spraying compressed air with water as a low-temperature heat source for compressor intercoolers and post-coolers in gas turbine power generation equipment. Examples using humidified air have been reported. In addition, in the above-mentioned document (hereinafter referred to as a prior art), water which is sprayed with water droplets on raw air is divided into humidified and cooled air, and one is taken out as it is, and the other is heat-exchanged with raw air to exchange raw air. A method is described in which the temperature of air after humidification and temperature reduction is lowered by lowering the temperature of the air.

[0004]

In the above-mentioned prior art, when the temperature of the raw material air is high, the temperature of the humidified air after spraying water is also high. For example, heat exchange is performed from turbine exhaust gas in a gas turbine cycle. When used as a medium for wastewater, exhaust heat cannot be sufficiently recovered, and plant efficiency may remain low.

[0005] An object of the present invention is to provide a gas turbine system in which the power generation efficiency of a plant is improved.

[0006]

To achieve the above object, a gas turbine system according to the present invention comprises a compressor for compressing air, and a combustor for burning air and fuel compressed by the compressor. A gas turbine driven by combustion exhaust gas generated in the combustor, and a regenerative heat exchanger for exchanging heat between the gas turbine exhaust gas discharged from the gas turbine and compressed air guided to the combustor A first humidifier for humidifying a first air compressed and branched by the compressor, a first air humidified by the first humidifier, and a branch at the branch device. A heat exchanger for exchanging heat with the second air, and a second humidifier for humidifying the second air heat exchanged by the heat exchanger, wherein the first and second air are It is guided to the regenerative heat exchanger To. Also, a compressor for compressing air, a combustor for burning air and fuel compressed by the compressor, a gas turbine driven by combustion exhaust gas generated in the combustor, and a gas turbine discharged from the gas turbine A heat recovery heat exchanger for exchanging heat between the gas turbine exhaust gas and the compressed air guided to the combustor; and humidifying the air compressed and branched into a plurality of pieces by the compressor to different temperatures, respectively. Comprising a plurality of humidifiers leading to the heat recovery heat exchanger, of the humidified air guided to the heat recovery heat exchanger, the lower temperature humidified air to the gas turbine exhaust gas downstream position of the heat recovery heat exchanger. It is characterized by leading.

[0007]

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

FIG. 1 is a system diagram of a gas turbine system according to an embodiment of the present invention.

The gas turbine system of this embodiment shown in FIG. 1 mixes a fuel 1 with a compressor 1 for compressing air 10, humidified air 140 humidified by compressed air from the compressor, and burns. A combustor 5 for generating gas, a turbine 7 operated by combustion gas from the combustor 5,
, A generator 20 for converting the mechanical energy into electric energy to generate electric power, generating electricity, a regenerative heat exchanger 3 for recovering heat of the exhaust gas 8 discharged from the turbine 7, and an exhaust gas also discharged from the turbine 7. A feed water heater 9 for heating feed water by utilizing heat of the gas 8 and a motor (which is connected to the turbine and rotates the turbine until fuel is supplied to the combustor and the turbine can operate independently) ( A starter 25 and a branch device 30 that branches the compressed air 101 compressed by the compressor 1 and changes the branch ratio (distribution of the discharge flow rate of the compressed air).

In the present embodiment, the water recovery tower 13 for removing moisture in the exhaust gas 8a discharged from the feed water heater 9 is used.
A gas / gas heat exchanger 12 for exchanging heat between the exhaust gas 8b from which moisture has been removed by the water recovery tower 13 and the exhaust gas 8a discharged from the feed water heater 9, and an exhaust gas from which moisture has been recovered. A chimney 29 for discharging 8b into the atmosphere, a seawater pump 14 for pumping seawater, a condensate pump 15 for increasing the pressure of the recovered water recovered by the water recovery tower 13, a water treatment device 16 for purifying the recovered water, Collected water (hereinafter referred to as “water supply”)
And a water supply pump 17 for increasing the pressure of the water and supplying the water to the water heater 9. Further, in the present embodiment shown in FIG. 1, a first sprayer (humidifying device) for injecting or spraying water or steam (cooling medium) into the compressed air 110 branched by the branching device 30.
21 and a second atomizer (humidifier) 22 for injecting or spraying water or steam (cooling medium) into the other compressed air 130 branched by the branching device 30. Compressed air 103 and the first atomizer 21
A heat exchanger 23 for exchanging heat with the compressed air humidified by the above is provided. Note that the first sprayer 21 and the second sprayer 2
2 is supplied with feedwater heated by a feedwater heater 9 via a feedwater pump 18.

In the embodiment constructed as described above, first, the air 10 taken in from the outside air is compressed by the compressor 1 to become compressed air 101. The compressed air 101 is supplied to the branching device 3
At 0, the air is branched into compressed air 110 and compressed air 130.
The compressed air 110 is introduced into the first atomizer 21, in which a vaporizable amount of water is sprayed and humidified into the compressed air in the atomizer 21. Here, when the water is sprayed by the atomizer 21, latent heat of evaporation for vaporizing the water from the compressed air 110 is deprived, so that the temperature of the compressed air 110 is reduced. Therefore,
The outlet air of the atomizer 21 contains more moisture than the compressed air 110 introduced into the atomizer 21 and becomes humidified air 111 having a low temperature. The humidified air 111 whose temperature has decreased is supplied to the heat exchanger 23.

In the heat exchanger 23, the other compressed air 130 branched by the branching device 30 is guided, and heat exchange is performed between the compressed air 130 and the humidified air 111 humidified by the sprayer 21. Since the temperature of the humidified air 111 is lower than that of the compressed air 130, the humidified air 111 is heated by the compressed air 130 in the heat exchanger 23 to become high-temperature humidified air 112. On the other hand, the compressed air 1 cooled in the heat exchanger 23
31 is introduced into the second atomizer 22. In the atomizer 22, water is sprayed on the compressed air 131 by an amount that can be vaporized, and the low-temperature humidified air 132 is formed.

The low-temperature humidified air 13 humidified by the atomizer 22
2 is introduced into the regenerative heat exchanger 3 from the downstream side of the gas turbine exhaust gas, where heat exchange is performed with the gas turbine exhaust gas 8 to increase the temperature. Further, the high-temperature humidified air 112 heated by the heat exchanger 23 is supplied from the regenerative heat exchanger 3 to the gas turbine exhaust gas upstream from the position where the low-temperature humidified air 132 is introduced.
And mixed with the low-temperature humidified air 132 having a higher temperature to recover the exhaust heat of the gas turbine. The high-temperature humidified air 150 heated by the regenerative heat exchanger 3 is introduced into the combustor 5 and is used as a fuel supporting agent for the fuel 6 and / or a combustor cooling air.

The high-temperature and high-pressure combustion gas discharged from the combustor 5 is introduced into a gas turbine, and the turbine 7 is rotated to generate power by rotating a generator 20 connected to the turbine 7. Further, since the gas turbine exhaust gas 8 exiting the turbine 7 has a high temperature, the gas is used for preheating a humidified air or the like for use as a combustion supporting agent in the combustor, cooling air for the combustor, or both.

Further, the water used in the atomizers 21 and 22 is preheated by the feed water heater 9 provided downstream of the gas turbine exhaust gas rather than the regenerative heat exchanger 3 to recover heat from the gas turbine exhaust gas. Good. Here, the branching ratio of the high-temperature compressed air 101 and the flow rate of the spray water used in the first sprayer 21 and the second sprayer 22 can be adjusted. It is possible to generate humidified air 112 and cold humidified air 132. Although not shown, the temperature can be lowered by further spraying water on the high-temperature humidified air 112.

As described above, according to the present embodiment, the compressor 1
Even if the outlet air temperature is relatively high, humidified air with different temperatures including humidified air with a lower temperature than before can be generated by branching the compressor discharge air and then performing water spray and heat exchange. Therefore, it is possible to generate low-temperature humidified air using high-temperature air, and it is possible to recover heat from the gas turbine exhaust gas to a sufficiently low temperature in the regenerative heat exchanger 3, thereby increasing the power generation efficiency of the plant. There is an effect that can be. Further, it is possible to change the load of the gas turbine power generation system by changing the humidification amount in the atomizers 21 and 22 and the branching ratio in the downstream side of the heat exchanger. The system can be simplified and the cost can be reduced as compared with a gas turbine power generation system that uses a device to humidify and cool the compressor outlet air.

FIG. 2 shows the relationship between the amount of branching of the compressed air of this embodiment shown in FIG. In FIG. 2, the horizontal axis represents the flow rate of the divided compressed air 130 with respect to the total compressed air amount at the compressor outlet in percentage, and the vertical axis represents the plant flow rate when the flow rate of the compressed air 130 is 0. The increase in the power generation efficiency is shown as a relative value. The flow rate of the compressed air 130 is 0
In the case of, the case where only the temperature reducing humidification in the sprayer 20 is performed without branching is shown. 2A shows the flow rate of the compressed air 110 branched from the compressed air 101,
(B) shows the flow rate of the other branched compressed air 130.

As shown in FIG. 2, the increase in the power generation efficiency of the plant increases as the flow rate of the compressed air 130 increases. However, the flow rate of the compressed air 130 becomes maximum near 50%, and the flow rate increases more than 50%. As the power consumption increases, the increase in power generation efficiency decreases. Therefore, in order to increase the power generation efficiency of the plant, it is preferable to set the flow rate of the compressed air B to around 50%.

Next, a comparison between the conventional humidifying and cooling apparatus and the present embodiment under the same conditions will be described with reference to FIG.
In the figure, 40 is a heat exchanger, 41 is a sprayer, 150 is high-temperature air, 151 and 152 are low-temperature humidified air, and 153 is low-temperature humidified air.

In the conventional humidifying and cooling apparatus shown in FIG. 3, the entire amount of the high-temperature air 150 of, for example, about 300 ° C. is exchanged with the humidified and cooled air 151 to lower the temperature of the high-temperature air. At this time, the low-temperature humidified air 151 and the low-temperature humidified air
Assuming that the ratio of H.sub.2 to H.sub.2 is 1: 1, the flow rate of the high-temperature air 150 is about twice the flow rate of the low-temperature humidified air 151, so that the air temperature at the outlet of the heat exchanger 23 (the side to be cooled) is Considering the temperature efficiency of the above, it is about 210 ° C. Therefore, the temperature of the low-temperature humidified air obtained by cooling the air at about 210 ° C. by spraying water remains at about 113 ° C.

On the other hand, according to the embodiment shown in FIG. 1, compressed air 101 having a high temperature of, for example, about 300 ° C.
Branch to 1. One of the branched high-temperature compressed air 11
By humidifying and reducing the temperature of 0 with the first sprayer 21, it is possible to generate humidified air at about 125 ° C. Further, since the branched high-temperature compressed air 130 (about 300 ° C.) exchanges heat with the humidified air 111 (about 125 ° C.) having substantially the same flow rate, the temperature is reduced to about 140 ° C. About 140
By spraying water with the second atomizer 22 on the compressed air 131 at a low temperature of about 100 ° C., about 100
It is possible to obtain the low temperature humidified air 132 ° C.

FIG. 4 shows a second embodiment of the present invention. In the present embodiment shown in FIG.
1 is divided into high, medium and low temperature and three-stage humidified air. In the present embodiment, the high-temperature compressed air 101 compressed by the compressor 1 is first branched into two routes by the first branching device 30. One of the branched compressed air 110 is humidified by the first atomizer 21. The humidified air 111 humidified by the sprayer 21 and cooled to a low temperature is led to the heat exchanger 23, where the heat is exchanged with the high-temperature compressed air 130 branched to the other route by the branching device 30, and the high-temperature humidified air 112 Becomes

Here, in this embodiment, the compressed air 130 branched by the branching device 30 passes through the heat exchanger 23 and is then branched again into two routes by the second branching device. One of the compressed air 120 branched by the branching device 30
Is guided to the second sprayer 22 and humidified. Sprayer 2
The humidified air 121 humidified in 2 is supplied to the second heat exchanger 26 and exchanges heat with the other compressed air 140 branched by the second branching device 31. Since the compressed air 140 has a higher temperature than the humidified air 121, the humidified air 121 is heated to become the medium-temperature humidified air 122.

The other compressed air 140 branched as described above exchanges heat with the low-temperature humidified air 121 in the second heat exchanger 26 to lower the air temperature. Next, the compressed air 141 whose temperature has been reduced is guided to the third sprayer 24, where it is humidified, whereby the low-temperature humidified air 142 that is in a lower temperature state is obtained.

The low-temperature humidified air 142 obtained as described above
Is introduced to the downstream side of the gas turbine exhaust gas 8 of the regenerative heat exchanger 3, and heat recovery of the gas turbine exhaust gas 8 is performed. The medium-temperature humidified air 122 is supplied to the gas turbine exhaust gas upstream from the introduction point of the low-temperature humidified air 142, and is mixed with the low-temperature humidified air 142 having a higher temperature to further recover heat of the gas turbine exhaust gas. The high-temperature humidified air 112 is supplied further upstream from the introduction point of the medium-temperature humidified air 122,
Similarly, heat is recovered by being mixed with the low-temperature humidified air 142 and the medium-temperature humidified air 122.

As described above, according to the present embodiment, the temperature of the low-temperature humidified air 142 can be lower than that of the humidified air 121 humidified by the second atomizer 22, and the humidification reduction of the present embodiment can be reduced. If the high-temperature air introduced into the heating device is under the same conditions, it is possible to obtain humidified air at a lower temperature than the embodiment shown in FIG. Further, by further increasing the number of times of branching of the high-temperature air, that is, the number of heat exchangers, it becomes possible to obtain humidified air having a lower temperature.

Next, the effect of the embodiment shown in FIG. 4 will be described with reference to FIG. FIG. 5 is a diagram showing the relationship between the number of air branch stages and the low-temperature humidified air temperature. The high-temperature air in the figure was at an air temperature of 300 ° C and a relative humidity of 0.0%. At each branch point, the temperature-reduced air is branched 1: 1. Further, the vertical axis indicates the temperature of the humidified air having the lowest temperature among the humidified air having different temperatures generated by the humidifying and reducing device of the present invention. The horizontal axis indicates the number of times the humidified air is branched, and the branch indicates a series of flows in which the humidified air is branched, one of which is subjected to water spray cooling, and then heat exchange is performed with the other. Here, the humidified air refers to air that has not been humidified after being introduced into the humidifying and cooling device of the present embodiment. FIG. 5 shows that the temperature of the low-temperature humidified air can be lowered by increasing the number of times of branching of the air downstream of the heat exchanger. Branching downstream of the heat exchanger can generate humidified air at a temperature 30 to 70 ° C. lower than when no branching is performed.

Next, a gas turbine system according to a third embodiment of the present invention will be described with reference to FIG.

The efficiency of a gas turbine system for recovering heat of gas turbine exhaust gas using humidified air is, if other conditions are equal, the lower the temperature of the gas turbine exhaust gas released to the atmosphere after performing heat recovery. Get higher. In the gas turbine system shown in FIG. 1, the gas turbine exhaust gas temperature at the outlet of the regenerative heat exchanger 3 is 200 ° C. lower than that of the low-temperature humidified air 132 generated by the atomizer 22 which is a humidifying and cooling device.
Moderately high, further heat recovery is possible. Therefore, in the present embodiment shown in FIG. 6, a sprayer 4 for spraying water to the regenerative heat exchanger unit 3 and an intake sprayer 28 for spraying water to the compressor intake are installed in the gas turbine system of FIG. This is to recover water from the gas turbine exhaust gas 8.

In the gas turbine system of the present embodiment, the air 10 taken into the compressor 1 is first supplied to the intake atomizer 28.
The air 10 is cooled and humidified by spraying the air 10 with water. The dehumidified and humidified air is compressed by the compressor 1 to form compressed air 101. The compressed air 101 at the outlet of the compressor 1 is branched by the branching device 30 into compressed air 110 and compressed air 130. Branched compressed air 11
0 is introduced into the first atomizer 21, in which a vaporizable amount of water is sprayed into the compressed air 110 in the atomizer 21 and humidified. Further, latent heat of vaporization for evaporating water is compressed air 11.
Compressed air 110 is de-cooled to steal from zero. Therefore, the humidified air 111 that is the outlet air of the atomizer 21 contains more moisture than the compressed air 110 before humidification,
It becomes humidified air with low temperature. Since the temperature of the humidified air 111 is lower than that of the other branch of the compressed air 130, the humidified air 111 exchanges heat with the high-temperature compressed air 130 in the heat exchanger 23, and becomes high-temperature humidified air 112.

On the other hand, the compressed air 131 cooled in the heat exchanger 23 is introduced into the second atomizer 22. In the atomizer 22, water is sprayed on the compressed air 131 by an amount that can be vaporized, and the low-temperature humidified air 132 is formed. This low temperature humidified air 13
No. 2 is characterized in that the temperature is lower than that of the high-temperature humidified air 112. The low-temperature humidified air 132 is introduced into the regenerative heat exchanger 3 from the downstream side of the gas turbine exhaust gas, exchanges heat with the gas turbine exhaust gas 8 to increase the temperature, and
2 is introduced into the regenerative heat exchanger 3 from the upstream side of the gas turbine exhaust gas with respect to the introduction position of the low-temperature humidified air 132, and is mixed with the low-temperature humidified air 112 having a higher temperature to recover the exhaust heat of the gas turbine.

The high-temperature humidified air 150 heated by the regenerative heat exchanger 3 is introduced into the combustor 5 and used as a fuel-supporting agent for the fuel 6 or as cooling air for the combustor. The high-temperature and high-pressure combustion gas discharged from the combustor 5 is introduced into the gas turbine 7 and rotates the turbine to generate power by rotating a generator connected to the turbine. Furthermore, since the gas turbine exhaust gas 8 that has exited the turbine 7 has a high temperature, the gas is used for preheating humidified air or the like for use as a combustion support in a combustor. Also, the water used in the sprayers 21 and 22 may be preheated by the feedwater heater 9 and further heat recovery from the gas turbine exhaust gas. here,
Branching ratio of compressed air 100, atomizer 21 and atomizer 22
It is possible to adjust the flow rate of the spray water used in the process, and by adjusting these, it is possible to generate the high-temperature humidified air 112 and the low-temperature humidified air 132 having an appropriate temperature, humidity and flow rate according to the gas turbine load. It is. Also,
Although not shown, the temperature can be lowered by further spraying water on the high-temperature humidified air 112.

In general, if other conditions are the same, the efficiency of the gas turbine system is improved by lowering the temperature of the gas turbine exhaust gas discharged outside the system. In the fourth embodiment, one or more regenerative heat exchange sprayers 4 are installed in the regenerative heat exchanger 3, and the reheat exchanger 3 is preheated by a feed water heater 9 installed downstream of the gas turbine exhaust gas. The water thus obtained is sprayed onto the humidified air heated by the regenerative heat exchanger to reduce the temperature of the humidified air. As a result, the amount of gas turbine exhaust heat recovered in the regenerative heat exchanger increases, and the temperature of the gas turbine exhaust gas discharged from the system to the outside of the system can be reduced to an arbitrary temperature. However, since the temperature of the exhaust gas of the gas turbine at the outlet of the regenerative heat exchanger cannot be lower than the temperature of the humidified air on the heated side of the regenerative heat exchanger, the use of the low-temperature humidified air generated by the gas humidifying and dehumidifying device of the present invention is used. Is valid.

Further, by humidifying and reducing the temperature before introducing the air 10 into the compressor 1, the specific volume of the compressed air in the compressor is reduced, and the required power of the compressor 1 can be reduced. Further, in the gas turbine system of the present embodiment, the temperature of the high-temperature humidified air 112 at the outlet of the heat exchanger 23 decreases as the temperature of the compressed air at the compressor outlet decreases, and the amount of heat that can be recovered by the humidified air increases.

Further, in this embodiment, a large amount of water is contained in the gas turbine exhaust gas, and by discharging this to the atmosphere together with the gas turbine exhaust gas 8, a large amount of water is newly required. The water used in the intake atomizer 28, the atomizers 21 and 22, and the atomizer 4 installed in the regenerative heat exchanger 3 of the gas turbine system of the present embodiment becomes a high-temperature gas turbine working fluid after being vaporized. It is necessary to perform water treatment so as not to shorten the life of the gas turbine.
Therefore, in the present invention, the water in the gas turbine exhaust gas 8 is
By collecting the water in the water recovery tower 13 before releasing it to the atmosphere, it is possible to operate the system without having to supply new water from outside the system.

FIG. 7 shows a comparison of the effect of the gas turbine cycle of the present embodiment with respect to the humidifying and cooling characteristics with respect to the case where the conventional humidifying and cooling device is applied to a gas turbine cycle. In this study, the compressed air condition (temperature: about 300 ° C., pressure: about 1
(5 kg / cm ² , moisture: about 4 vol%).

The vertical axis of the drawing shows the temperature of the low-temperature humidified air and the low-temperature region heat recovery capacity (relative value) obtained by each method. The purpose of obtaining the low-temperature humidified air here is to enable the heat recovery of the gas turbine exhaust heat to as low a temperature as possible, and it is desirable to use a method that can obtain a large amount of low-temperature air. Therefore, in order to compare the heat recovery capacity of each system in a region where the temperature of the exhaust gas of the gas turbine is relatively low, the heat recovery capacity in a low-temperature region is defined by the following equation.

Low-temperature region heat recovery capacity = flow branch ratio to low-temperature humidified air side × (gas turbine exhaust gas temperature near regenerator outlet-low-temperature humidified air temperature) As shown in FIG. The low-temperature region heat recovery capacity defined above becomes maximum near the flow branching ratio of 50% at the branching point. However, since the low-temperature humidified air temperature increases with the increase in the flow branching ratio, the increase in the low-temperature region heat recovery capacity is relatively small.

On the other hand, also in the method of the present embodiment, the low-temperature region heat recovery capacity defined in the previous term becomes maximum near the flow branching ratio of 50%. The low-temperature humidified air temperature in this embodiment is:
The flow branching rate is constant at approximately 100 ° C. up to about 50%. When the flow branching ratio is about 50%, the temperature of the humidified air on the low-temperature side can be lowered as compared with the prior art. Therefore, there is a merit that the low-temperature region heat recovery ability is increased as compared with the conventional technology.

Therefore, in the gas turbine cycle of the present embodiment, the heat recovery capacity in the low temperature region can be increased as compared with the case where the humidifying and dehumidifying device of the prior art is applied, and the heat recovery from the gas turbine exhaust gas can be performed at a low temperature. Therefore, there is an effect that the power generation efficiency of the plant can be increased. Further, when the present embodiment is applied, since the temperature of the low-temperature humidified air can be further reduced by configuring the number of the branching stages of the compressed air to two or more, the heat from the gas turbine exhaust gas is reduced. There is a possibility of further recovery and further improvement of power generation efficiency.

Further, when the gas turbine exhaust gas temperature at the outlet of the regenerator heat exchanger 3 is equal to or higher than a certain temperature, the temperature difference between the gas turbine exhaust gas and the humidified and de-heated air can be increased. There is an effect that it can be reduced.

[0042]

According to the present invention, since it is possible to recover the heat of gas turbine exhaust gas to a low temperature, it is possible to provide a gas turbine system with improved power generation efficiency of a plant.

[Brief description of the drawings]

FIG. 1 is a system diagram of a gas turbine system according to an embodiment of the present invention.

FIG. 2 is a diagram showing a relationship between a flow rate ratio of branched compressed air and a high rate increase.

FIG. 3 is a system diagram of a conventional gas turbine system.

FIG. 4 is a system diagram of a gas turbine system according to a second embodiment of the present invention.

FIG. 5 is a diagram showing the relationship between the number of branches of compressed air and the temperature of low-temperature humidified air.

FIG. 6 is a system diagram of a gas turbine system according to a third embodiment of the present invention.

FIG. 7 is a diagram showing a relationship between a flow branch ratio of compressed air, a low-temperature humidified air temperature, and a low-temperature region heat recovery capacity.

[Explanation of symbols]

1 ... compressor, 3 ... regenerative heat exchanger, 4 ... regenerative heat exchange sprayer,
5: Combustor, 6: Fuel, 7: Turbine, 8: Gas turbine exhaust gas, 9: Feed water heater, 10: Air, 11: Compressed air, 12: Gas / gas heat exchanger, 13: Water recovery tower, 14
... seawater pump, 15 ... condensate pump, 16 ... water treatment device,
17, 18: feed pump, 20: generator, 21, 22, ...
Atomizer, 23 heat exchanger, 30, 31 branching device, 11
2: high temperature humidified air, 132: low temperature humidified air.

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[Procedure amendment]

[Submission date] December 14, 1999 (1999.12.
14)

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] 0009

[Correction method] Change

[Correction contents]

The gas turbine system of this embodiment shown in FIG. 1 mixes a compressor 1 for compressing air 10, a humidified air 150 in which the compressed air from the compressor is humidified, and a fuel 6 for combustion. A combustor 5 for generating gas, a turbine 7 operated by combustion gas from the combustor 5,
, A generator 20 for converting the mechanical energy into electric energy to generate electric power, generating electricity, a regenerative heat exchanger 3 for recovering heat of the exhaust gas 8 discharged from the turbine 7, and an exhaust gas also discharged from the turbine 7. A feed water heater 9 for heating feed water by utilizing heat of the gas 8 and a motor (which is connected to the turbine and rotates the turbine until fuel is supplied to the combustor and the turbine can operate independently) ( A starter 25 and a branch device 30 that branches the compressed air 101 compressed by the compressor 1 and changes the branch ratio (distribution of the discharge flow rate of the compressed air).

[Procedure amendment 2]

[Document name to be amended] Statement

[Correction target item name] 0010

[Correction method] Change

[Correction contents]

In the present embodiment, the water recovery tower 13 for removing moisture in the exhaust gas 8a discharged from the feed water heater 9 is used.
A gas / gas heat exchanger 12 for exchanging heat between the exhaust gas 8b from which moisture has been removed by the water recovery tower 13 and the exhaust gas 8a discharged from the feed water heater 9, and an exhaust gas from which moisture has been recovered. A chimney 29 for discharging 8b into the atmosphere, a seawater pump 14 for pumping seawater, a condensate pump 15 for increasing the pressure of the recovered water recovered by the water recovery tower 13, a water treatment device 16 for purifying the recovered water, Collected water (hereinafter referred to as “water supply”)
And a water supply pump 17 for increasing the pressure of the water and supplying the water to the water heater 9. Further, in the present embodiment shown in FIG. 1, a first sprayer (humidifying device) for injecting or spraying water or steam (cooling medium) into the compressed air 110 branched by the branching device 30.
21 and a second atomizer (humidifier) 22 for injecting or spraying water or steam (cooling medium) into the other compressed air 130 branched by the branching device 30. Compressed air 130 and the first atomizer 21
A heat exchanger 23 for exchanging heat with the compressed air humidified by the above is provided. Note that the first sprayer 21 and the second sprayer 2
2 is supplied with feedwater heated by a feedwater heater 9 via a feedwater pump 18.

[Procedure amendment 3]

[Document name to be amended] Statement

[Correction target item name] 0017

[Correction method] Change

[Correction contents]

[0017] Figure 2, the compressed air branching of this embodiment shown in FIG. 1, there is shown a branch amount and efficiency increase of the relationship. In FIG. 2, the horizontal axis represents the flow rate of the divided compressed air 130 with respect to the total compressed air amount at the compressor outlet in percentage, and the vertical axis represents the plant flow rate when the flow rate of the compressed air 130 is 0. The increase in the power generation efficiency is shown as a relative value. The flow rate of the compressed air 130 is 0
In the case of, the case where only the temperature reducing humidification in the sprayer 20 is performed without branching is shown. 2A shows the flow rate of the compressed air 110 branched from the compressed air 101,
(B) shows the flow rate of the other branched compressed air 130.

[Procedure amendment 4]

[Document name to be amended] Statement

[Correction target item name] 0019

[Correction method] Change

[Correction contents]

Next, a comparison between the conventional humidifying and cooling apparatus and the present embodiment under the same conditions will be described with reference to FIG.
40 heat exchanger shown in the figure, 41 is the atomizer, 150 hot air, 151 and 152 low-temperature humidified air, 153 shows a Atsushi Ko air.

[Procedure amendment 5]

[Document name to be amended] Statement

[Correction target item name] 0033

[Correction method] Change

[Correction contents]

In general, if other conditions are the same, the efficiency of the gas turbine system is improved by lowering the temperature of the gas turbine exhaust gas discharged outside the system. In this embodiment , one or a plurality of regenerative heat exchange sprayers 4 are installed in the regenerative heat exchanger 3, and the regenerative heat exchanger 3
Feed water heater 9 installed downstream of the gas turbine exhaust gas
Is sprayed onto the humidified air heated by the regenerative heat exchanger to reduce the temperature of the humidified air. As a result, the amount of gas turbine exhaust heat recovered in the regenerative heat exchanger increases, and the temperature of the gas turbine exhaust gas discharged from the system to the outside of the system can be reduced to an arbitrary temperature. However, the gas turbine exhaust gas temperature at the outlet of the regenerative heat exchanger cannot be lower than the humidified air temperature on the heated side of the regenerative heat exchanger.
It is effective to use low-temperature humidified air generated by the gas humidification / temperature-reducing device of the present invention.

[Procedure amendment 6]

[Document name to be amended] Statement

[Correction target item name] Brief description of drawings

[Correction method] Change

[Correction contents]

[Brief description of the drawings]

FIG. 1 is a system diagram of a gas turbine system according to an embodiment of the present invention.

[Figure 2] relationship diagram between flow rate and efficiency increase of the compressed air branching.

FIG. 3 is a system diagram of a conventional gas turbine system.

FIG. 4 is a system diagram of a gas turbine system according to a second embodiment of the present invention.

FIG. 5 is a diagram showing the relationship between the number of branches of compressed air and the temperature of low-temperature humidified air.

FIG. 6 is a system diagram of a gas turbine system according to a third embodiment of the present invention.

FIG. 7 is a diagram showing a relationship between a flow branch ratio of compressed air, a low-temperature humidified air temperature, and a low-temperature region heat recovery capacity.

[Description of Signs] 1 ... Compressor, 3 ... Regenerative heat exchanger, 4 ... Regenerative heat exchange sprayer,
5: Combustor, 6: Fuel, 7: Turbine, 8: Gas turbine exhaust gas, 9: Feed water heater, 10: Air, 11: Compressed air, 12: Gas / gas heat exchanger, 13: Water recovery tower, 14
... seawater pump, 15 ... condensate pump, 16 ... water treatment device,
17, 18: feed pump, 20: generator, 21, 22, ...
Atomizer, 23 heat exchanger, 30, 31 branching device, 11
2: high temperature humidified air, 132: low temperature humidified air.

Continued on the front page (72) Inventor Yoshiki Noguchi 3-1-1, Sakaimachi, Hitachi-shi, Ibaraki Pref. Hitachi, Ltd. Thermal and Hydropower Division (72) Inventor Shigeo Hatamiya 7-2 Omikacho, Hitachi City, Ibaraki Prefecture No. 1 Inside Power & Electric Development Laboratory, Hitachi, Ltd.

Claims (9)

[Claims] 1. A compressor for compressing air, a combustor for burning air and fuel compressed by the compressor, a gas turbine driven by combustion exhaust gas generated in the combustor, and the gas turbine And a regenerative heat exchanger for exchanging heat between the gas turbine exhaust gas discharged from the compressor and the compressed air guided to the combustor, wherein the first air compressed and branched by the compressor is provided. A first humidifier for humidifying, and a first humidifier humidified by the first humidifier.
And a heat exchanger for exchanging heat with the second air branched from the compressor, and a second humidifier for humidifying the second air heat-exchanged by the heat exchanger, The gas turbine system according to claim 1, wherein the first and second air are guided to the regenerative heat exchanger. 2. A compressor for compressing air, a combustor for burning air and fuel compressed by the compressor, a gas turbine driven by combustion exhaust gas generated in the combustor, and the gas turbine. A heat recovery heat exchanger for exchanging heat between the gas turbine exhaust gas discharged from the compressor and the compressed air guided to the combustor, and humidifying each of the plurality of branched air compressed by the compressor to different temperatures, A plurality of humidifiers for guiding the humidified air to the heat recovery heat exchanger, and among the humidified air guided to the heat recovery heat exchanger, the humidified air having a lower temperature is disposed downstream of the heat recovery heat exchanger in the gas turbine exhaust gas. A gas turbine system, which is directed to a side position. 3. A compressor for compressing air, a combustor for burning air and fuel compressed by the compressor, a gas turbine driven by combustion exhaust gas generated in the combustor, and the gas turbine. And a heat recovery heat exchanger for exchanging heat between the gas turbine exhaust gas discharged from the compressor and the compressed air guided to the combustor, wherein the first air compressed and branched by the compressor is provided. And a first humidifier for guiding the humidified first air to the heat recovery heat exchanger, and humidifying the second air branched from the compressor to a temperature lower than that of the first air. And a second humidifier for guiding the first air to a heat recovery heat exchanger at a position downstream of the gas turbine exhaust gas. 4. A compressor for compressing air, a combustor for burning air and fuel compressed by the compressor, a gas turbine driven by combustion exhaust gas generated in the combustor, and the gas turbine A gas turbine system having a regenerative heat exchanger that exchanges heat between gas turbine exhaust gas discharged from the compressor and compressed air guided to the combustor, and a branching device that branches the air compressed by the compressor. A first humidifier for humidifying the first air branched by the branching device; a first air humidified by the first humidifier;
A heat exchanger for exchanging heat with the second air branched by the branching device, and a second humidifying device for humidifying the second air heat exchanged by the heat exchanger; The second air humidified by the humidifier is guided to the regenerative heat exchanger, and the first air humidified by the first humidifier and passed through the heat exchanger is guided to the regenerative heat exchanger. A gas turbine system characterized in that the gas is supplied to the gas turbine exhaust gas upstream from the air. 5. A compressor for compressing air, a combustor for burning air and fuel compressed by the compressor, a gas turbine driven by combustion exhaust gas generated in the combustor, and the gas turbine. A gas turbine system having a regenerative heat exchanger that exchanges heat between gas turbine exhaust gas discharged from the compressor and compressed air guided to the combustor, and a branching device that branches the air compressed by the compressor. A first humidifier for humidifying the first air branched by the branching device; a first air humidified by the first humidifier;
A heat exchanger for exchanging heat with the second air branched by the branching device, a second humidifying device for humidifying the second air heat exchanged by the heat exchanger, and taken into the compressor A third humidifier for humidifying the intake air, wherein the first and second humidifiers are provided.
Wherein the air is guided to the regenerative heat exchanger. 6. A compressor for compressing air, a combustor for burning air and fuel compressed by the compressor, a gas turbine driven by combustion exhaust gas generated in the combustor, and the gas turbine Turbine system having a regenerative heat exchanger for exchanging heat between a gas turbine exhaust gas discharged from a compressor and compressed air guided to the combustor, wherein a first branch for branching the air compressed by the compressor is provided. An apparatus, a first humidifier for humidifying the first air branched by the first diverter, a first air humidified by the first humidifier, and a first humidifier. A first heat exchanger for exchanging heat with the branched second air, a second branching device for branching the second air heat-exchanged by the first heat exchanger, and Second humidifying the second air passing through the branching device
A humidifier, a second heat exchanger that exchanges heat between the second air humidified by the second humidifier, and the third air branched by the second branching device, A third humidifier that humidifies the third air that has passed through the second heat exchanger, guiding the third air humidified by the third humidifier to the regenerative heat exchanger, The second air humidified by the humidifier and passed through the second heat exchanger is guided to the gas turbine exhaust gas upstream of the third air guided to the regenerative heat exchanger, and humidified by the first humidifier. A gas turbine system, wherein the first air that has passed through the first heat exchanger is guided to a gas turbine exhaust gas upstream of the second air that is guided to the regenerative heat exchanger. 7. The gas turbine according to claim 1, wherein the flow rate of the first air is branched to 40 to 60% with respect to the compressed air compressed by the compressor. Turbine system. 8. The gas turbine system according to claim 1, wherein said regenerative heat exchanger includes a sprayer for spraying water or steam to said first air or second air supplied to said regenerative heat exchanger. A gas turbine system comprising: 9. The gas turbine system according to claim 1, wherein the first humidifying device or the second humidifying device utilizes the gas turbine exhaust gas discharged from the regenerative heat exchanger.
A gas turbine system comprising a feedwater heater for heating water or steam supplied to a humidifying device.