JP2000282895A - Intake air cooling device and method for gas turbine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an efficient intake air cooling system for a gas turbine by effectively using accumulated cold for cooling intake air. SOLUTION: Intake air 21 is cooled by making cooling water pass through an intake air cooler 20 which is installed in a gas turbine intake air passage. The cooling water is cooled by brine via an intermediate heat exchanger 24. The brine is supplied from a heat storage tank 27, stored at a low temperature, by freezing water by a refrigerator 28 at night. In this case, the cooling quantity of the intake air 21 is adjusted, by transmitting the signals of the temperature and humidity of the intake air 21 downstream of the intake air cooler 20 to a calculator 31 and controlling a brine flow control valve 26, an auxiliary brine flow control valve 35 and brine circulation pump 33, based on the signals processed in the calculator 31.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gas turbine intake cooling system applied to, for example, a combined cycle power plant.

[0002]

2. Description of the Related Art In recent years, instead of a thermal power plant using a single steam turbine or a single gas turbine as a prime mover, a combined cycle power plant that has a combination of both advantages has been used. A combined cycle power plant is a combination of different cycles that operate in a high-temperature range and a low-temperature range.The high-temperature side cycle uses the Brayton cycle of a gas turbine that uses the combustion heat of fuel as a heat source, and the low-temperature side cycle uses The use of a Rankine cycle that uses the residual heat of the combustion gas exhaust, which is the working medium of the high-temperature side cycle, as a heat source improves overall thermal efficiency. That is, the combined cycle power plant utilizes the advantages of a high maximum use temperature of a gas turbine and a low minimum cycle use temperature of a steam turbine by combining two cycles of gas turbine power generation and steam power generation. It was done. FIG. 7 shows an example of a system configuration of a general exhaust heat recovery type combined cycle power plant. Waste heat from the gas turbine 3 connected to the compressor 1 and the combustor 2
The steam generated by the heat recovery is supplied to a steam turbine 5 to drive it. In FIG. 7, 6 is a generator, 7 is a condenser, and 8 is a condensate pump for supplying condensate to the exhaust heat recovery boiler 4.

[0003] Such a combined cycle power plant has the following advantages: a) high thermal efficiency; b) little decrease in thermal efficiency at partial load; c) short start-up time; and d) maximum output. It also has the disadvantage that it changes depending on the outside air temperature. The gas turbine 3 is operated by setting the upper limit of the combustion gas temperature of the first stage of the gas turbine from the viewpoint of durability of the blades in a high temperature range. On the other hand, since the volume of air that can be sucked by the compressor 1 is substantially constant, when the air temperature is decreased and the air density is increased, the mass of air that can be sucked is increased. Further, since the temperature of the compressed air also decreases due to the decrease in the suction temperature of the compressor 1, the heating range up to the upper limit value of the combustion gas temperature at the inlet of the gas turbine 3 increases, and a synergistic effect with the increase in the suction air amount. As a result, more fuel can be supplied, and the maximum output of the gas turbine 3 increases. Regarding the steam turbine 5, the amount of steam generated by the exhaust heat recovery boiler 4 slightly increases due to the increase in the amount of exhaust gas from the gas turbine 3 due to the decrease in the atmospheric temperature, and the maximum output also increases.
That is, the maximum output of the combined cycle power plant increases as the atmospheric temperature decreases.

FIG. 8 shows the relationship between the maximum output of a combined cycle power plant and the atmospheric temperature, taking a single-shaft type as an example. In the figure, the horizontal axis represents the atmospheric temperature, and the vertical axis represents the axial output when the atmospheric temperature is 0 ° C., that is, the value when the sum of the gas turbine output and the steam turbine output is 100. According to FIG. 8, the output decreases as the atmospheric temperature increases, and at an atmospheric temperature of 40 ° C., it drops to about 82% of that at 0 ° C. This means that the output of the combined cycle power plant decreases during the daytime in summer when the power demand is highest. In order to improve such characteristics, it is effective to cool the intake air entering the compressor 1. For example, a method of cooling intake air using cold water has been proposed, and this technique is disclosed in Japanese Patent Application Laid-Open No. 9-195797. FIG. 9 is a diagram showing a combined cycle power plant including the above. The same parts as those in FIG. 7 are denoted by the same reference numerals, and detailed description thereof will be omitted. As shown in FIG. 9, this technique employs an intake duct 9
The intake air is cooled by passing the cold water produced by the cold water producing device 18 through the cold water coil 10 provided therein. However, since the temperature and humidity of the intake air change every day and over time and are not constant, the intake air temperature and the intake air humidity at the outlet of the intake air cooler also change according to the intake air condition at the inlet. Therefore, depending on the temperature and humidity of the intake air,
There is a problem that the outlet intake air is supercooled and dew condensation occurs on the heat transfer tube surface. The large condensed heat generated at this time does not contribute to the cooling of the intake air, and the cold heat is taken away, resulting in a loss. Therefore, in the above publication, the intake thermometer 16, the atmospheric thermometer 14, and the atmospheric humidity meter 15 are used.
The signals from these sensors are calculated by a calculator 17 and the chilled water control valve 12 and the bypass valve 13 are controlled to remove only the sensible heat of the air sucked into the intake duct 9, and this cooling is performed. The used air is configured to be used as gas turbine intake air of a combined cycle power generation system.

[0005]

However, at the time of starting the gas turbine 3 or the like, the chilled water producing device 18 may not operate sufficiently, and the effect of intake air cooling may not be fully exerted. In addition, since energy is also required for cold water production, especially during the summertime when power demand peaks,
The energy used for producing the cold water is also lost.
Further, as described above, the peak of the power demand occurs during the daytime in summer, and even in the summertime, the peak output is often not required in the nighttime as at the peak time. The present invention has been made in view of such circumstances, and an object of the present invention is to provide an intake air cooling device for a gas turbine that enables setting of an intake air temperature in accordance with power demand, thereby having excellent operation controllability. .

[0006]

According to the first aspect of the present invention, there is provided a heat storage tank for storing ice produced by operating a refrigeration cycle, and for storing cold heat stored in the heat storage tank. Means for cooling the intake air in the intake flow path of the gas turbine compressor by using the above-described configuration.By this configuration, when the power demand is low, ice is stored in the heat storage tank,
This ice can be used as a cold heat source to cool the intake of the gas turbine, so that not only can the maximum output be generated when the load demand of the gas turbine is high,
A good intake air cooling effect can be obtained. According to the second aspect of the present invention, an intake air cooler is provided in the intake passage of the gas turbine compressor and cools intake air by heat exchange with cooling water, and a heat storage device that stores ice produced by operating a refrigeration cycle. Tank, and an intermediate heat exchanger for exchanging heat with the cold stored in the heat storage tank and the cooling water is installed between the heat storage tank and the intake air cooler. A cooling water circulation pump, a cooling water supply pipe, and a cooling water return pipe are connected to form a cooling water circulation system, and the intermediate heat exchanger and the heat storage tank are liquids having a lower freezing point than water. The brine is circulated through a brine circulating pump, a brine supply pipe, and a brine return pipe to form a brine circulating system, and the temperature of ice stored in the heat storage tank is low. To The excessive cold is transmitted to intake air cooler can be prevented.

[0007] According to the inventions described in claims 3 to 8,
In addition to the invention described in 1, the intake air temperature detector provided in the intake flow path, the intake humidity detector, and the brine temperature detector provided in the brine circulation system, the brine flow detector, or provided in the cooling water circulation system A signal from the cooling water temperature detector, the cooling water flow detector, and the like is processed by a computing unit, and based on an output signal from the computing unit, a brine circulating pump, a brine flow regulating valve, and an auxiliary brine flow regulating valve, Alternatively, the cooling water circulation pump, the cooling water flow control valve, and the auxiliary cooling water flow control valve are controlled. With this configuration, in addition to the effect of the first aspect of the invention, it is possible to control the temperature of the intake air after cooling the intake air. The invention according to claims 9 to 12 is characterized in that when the temperature of the ice stored in the heat storage tank is not so low, only the brine circulation system is installed, and the brine is directly led from the heat storage tank to the intake air cooler. With this configuration,
When the temperature of the ice stored in the heat storage tank is not so low, the configuration of the intake air cooling device can be simplified. According to the invention described in claims 13 and 14, pure water is supplied into an intake passage downstream of the intake cooling device for a gas turbine according to any one of claims 1 to 12, and fine-grained pure water is supplied from a spray nozzle to the intake passage. It is characterized by spraying into the flow path. With this configuration, it is possible to further increase the mass flow rate of the intake air after cooling the intake air.

In the invention according to claim 15, using the intake air cooling device according to any one of claims 1 to 14, ice produced by operating a refrigeration cycle using excess power at night is stored in a heat storage tank as cold heat. It is characterized by: In this way, by using the stored cold heat for intake air cooling, the output of the gas turbine can be maximized even in the daytime in summer when power demand is highest.

[0009]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 shows an intake air cooling device for a gas turbine according to a first embodiment of the present invention. Note that this embodiment is applied to a gas turbine of a combined cycle power plant, and the configuration of the entire system downstream of the compressor is the same as that shown in FIG. 7, so that illustration and description thereof are omitted. An intake air cooler 20 that cools intake air 21 by exchanging heat with cooling water is provided in an intake passage 19 of a compressor (not shown) of a gas turbine.
This intake air cooler 20, cooling water supply pipe 22 for cooling water circulation
a, a coolant return pipe 22b, an intermediate heat exchanger 24 provided between the coolant supply pipe 22a and the coolant return pipe 22b, and a coolant circulation system provided by a coolant circulation pump 32 provided in the middle of the coolant supply pipe 22a. 22. Ice produced by performing a refrigeration cycle operation of the refrigerator 28 at night or the like when power demand is low is stored in a heat storage tank 27 serving as a cold heat source of the intake air cooler 20. In addition, a heat storage tank as a cold heat source
27, brine supply pipe 25 that receives cold heat from heat storage tank 27
a, a brine return pipe 25b, an intermediate heat exchanger 24 provided between the brine supply pipe 25a and the brine return pipe 25b, and a brine circulation system 25 including a brine circulation pump 33 provided in the middle of the brine supply pipe 25a. It is configured. Here, as the brine, a liquid that does not freeze even with ice stored in the heat storage tank 27, such as ethylene glycol, is used.

In this embodiment, when the temperature of ice stored in the heat storage tank 27 is low, the amount of cold heat supplied to the heat transfer surface of the intake air cooler is prevented from being too large. A cooling water circulation system 22 is connected via an intermediate heat exchanger 24. An intake air temperature detector 29 and an intake humidity detector 30 are provided at an intake outlet of the intake air cooler 20. In the middle of the brine supply pipe 25a, a brine temperature detector 36
And a brine flow detector 37. Also,
A short circuit is provided between the brine supply pipe 25a and the brine return pipe 25b by a bypass pipe, and an auxiliary brine flow control valve 35 is provided on the way, and the brine return pipe 25b
In the middle of the process, a brine flow control valve 26 is installed. 31 is an arithmetic unit, an intake air temperature detector 29, an intake humidity detector
30, a signal from the brine temperature detector 36 and the brine flow rate detector 37 is inputted, and the calculation result is used to control the brine flow rate regulating valve 26, the auxiliary brine flow rate regulating valve 35, and the brine circulation pump 33. It is. The operation of this configuration is as follows. That is, during the daytime when the load demand of the combined cycle power generation system increases, the brine circulating pump 33 is started, and the cold stored in the brine in the heat storage tank 27 is sent to the intermediate heat exchanger 24 through the brine supply pipe 25a. The intermediate heat exchanger 24 exchanges heat with brine and cools the water in the cooling water circulation system 22. The brine whose temperature has risen due to heat exchange is
Is returned to the heat storage tank 27 and cooled again. The water cooled by the intermediate heat exchanger 24 is sent to the intake air cooler 20 by the cooling water circulation pump 32 via the cooling water supply pipe 22a. In this way, the intake air cooler 20 cools the intake air 21 guided from the intake air inlet. The cooling water whose temperature has increased due to heat exchange with the intake air 21 is supplied to the intermediate heat exchanger 2 by the cooling water return pipe 22b.
Return to 4 and cool again. At this time, the intake air temperature detector 2
9, the signals output from the intake humidity detector 30, the brine temperature detector 36 and the brine flow rate detector 37 are processed in the calculator 31, and the brine flow rate adjusting valve 2 is
6. The valve opening of the auxiliary brine flow control valve 35 and the output of the brine circulating pump 33 are adjusted, and the amount of cold heat sent to the intake air cooler 20 is controlled. At this time, by performing control so that the temperature of the intake air 21 after cooling is substantially equal to the dew point, it is possible to prevent the cold heat from being consumed as moisture contained in the intake air 21 as condensation heat.

Here, the flow rate control of the cooling water circulating pump 32 and the brine circulating pump 33 may be performed by controlling the number of revolutions by an inverter, or by controlling the number of pumps using a plurality of pumps. Also, intake air temperature detector
The intake air humidity detector 29 and the intake air humidity detector 30 may be installed at the intake air inlet of the intake air cooler 20. Further, two brine temperature detectors 36 may be provided one before and after the intermediate heat exchanger 24, that is, two in total. Further, the cooling water circulation pump 32 may be a constant flow type pump, and the cooling water circulation system 22 may be simplified. The amount of cold heat supplied to the intake air cooler 20 is controlled by a brine circulation pump.
33 is a constant flow type pump, and brine flow control valve 26
May be performed by adjusting the opening degree of the auxiliary brine flow rate adjustment valve 35, or without providing a bypass pipe and the auxiliary brine flow rate adjustment valve 35,
May be adjusted by adjusting the output. Further, in the first embodiment, the control performed in the brine circulation system 25 may be configured to be performed in the cooling water circulation system 22.
The configuration at this time is shown in FIG. The same parts as those in FIG. 1 are denoted by the same reference numerals, and detailed description thereof will be omitted.

That is, a cooling water flow control valve 23 is installed in the middle of the cooling water circulation system 22 to short-circuit the cooling water supply pipe 22a and the cooling water return pipe 22b by a bypass pipe, and to adjust the auxiliary cooling water flow rate on the way. A valve 34 is provided. 31 is a computing unit
Input signals from the intake air temperature detector 29, the intake air humidity detector 30, the cooling water temperature detector 39, and the cooling water flow detector 38, and calculate the cooling water flow adjusting valve 23, the auxiliary cooling water flow The control valve 34 and the cooling water circulation pump 32 are controlled. The operation of this configuration is as follows. That is, the brine circulation pump 33 is started, and the cold stored in the brine in the heat storage tank 27 is supplied to the brine supply pipe.
It is sent to the intermediate heat exchanger 24 by 25a. This intermediate heat exchanger 2
In 4, heat is exchanged between the brine and water, and the water in the cooling water circulation system 22 is cooled. The brine whose temperature has increased due to the heat exchange is returned to the heat storage tank 27 via the brine return pipe 25b, and is cooled again. The water cooled by the intermediate heat exchanger 24 is sent to the intake air cooler 20 by the cooling water circulation pump 32 via the cooling water supply pipe 22a. Thus, the intake air cooler 20 cools the intake air 21 guided from the intake air inlet. The cooling water whose temperature has increased due to heat exchange with the intake air 21 is returned to the intermediate heat exchanger 24 by the cooling water return pipe 22b, and is cooled again. On this occasion,
Signals output from the intake air temperature detector 29, the intake humidity detector 30, the cooling water temperature detector 39, and the cooling water flow rate detector 38 are processed in the calculator 31, and the cooling water flow rate adjusting valve 23, The valve opening of the cooling water adjustment valve 34 and the output of the cooling water circulation pump 32 are adjusted, and the amount of cold heat sent to the intake air cooler 20 is controlled. At this time, by performing control so that the temperature of the intake air 21 after cooling becomes substantially the dew point, it is possible to prevent the cool heat from being consumed as heat of condensation of the moisture contained in the intake air 21.

Here, the flow rate control of the cooling water circulating pump 32 and the brine circulating pump 33 may be performed by controlling the number of revolutions by an inverter, or by controlling the number of pumps using a plurality of pumps. Also, intake air temperature detector
The intake air humidity detector 29 and the intake air humidity detector 30 may be installed at the intake air inlet of the intake air cooler 20. Further, two cooling water temperature detectors 36 may be provided one before and after the intermediate heat exchanger 24, that is, two in total.
Also, the brine circulation pump 33 is a constant flow type pump,
The brine circulation system 25 may be simplified. Control of the amount of cold heat supplied to the intake air cooler 20 may be performed by adjusting the cooling water circulation pump 32 as a constant flow type pump and adjusting the opening of the cooling water flow adjustment valve 23 and the auxiliary cooling water flow adjustment valve 34. Alternatively, the adjustment may be performed by adjusting the output of the cooling water circulation pump 32 without providing the bypass piping and the auxiliary cooling water flow rate adjusting valve 34. Further, the brine circulation system 25 may be provided with a brine flow rate control valve 26, a bypass pipe for short-circuiting between the brine supply pipe 25a and the brine return pipe 25b, and an auxiliary brine flow rate control valve 35 in this bypass pipe. The configuration at this time is shown in FIG. The same parts as those in FIG. 2 are denoted by the same reference numerals, and detailed description thereof will be omitted.

As shown in FIG. 3, the cooling air supply capacity on the brine side is roughly determined in accordance with the cooling heat load by the brine flow rate adjusting valve 26, the auxiliary brine flow rate adjusting valve 35, and the brine circulating pump 33, and the intake air temperature detector 29. , Intake humidity detector 30, cooling water flow detector 38 and cooling water temperature detector
The signal from 39 is processed by the arithmetic unit 31 and the cooling water circulation system 22 performs fine adjustment of the intake air cooling capacity. With this configuration, the intake air cooling capacity can be adjusted widely and finely in accordance with the required change in the cooling capacity. In the first embodiment, when the temperature of the ice stored in the heat storage tank 27 is about 0 ° C. and is not so low, only the brine circulation system 25 is configured, and the brine from the heat storage tank 27 is discharged. Alternatively, it may be configured to directly perform intake air cooling. FIG. 4 shows a configuration example at this time. The same parts as those in FIG. 1 are denoted by the same reference numerals, and detailed description thereof will be omitted. As shown in FIG. 4, in this case, the heat storage tank 27, the intake air cooler
20, the brine supply pipe 25a, the brine return pipe 25b, and the brine circulating pump 33 constitute only the brine circulating system 25. Here, in the brine circulating system 25, a brine temperature detector 36, a brine flow detector 37, a brine flow control valve 26, a brine bypass pipe for short-circuiting the brine supply pipe 25a and the brine return pipe 25b, and the brine Auxiliary brine flow control valve in bypass piping
35 are provided. 31 is an arithmetic unit, intake air temperature detector 2
9. Input signals from the intake humidity detector 30, the brine temperature detector 36, and the brine flow detector 37, and calculate the brine flow adjustment valve 26, the auxiliary brine flow adjustment valve 35, and the brine circulation based on the calculation result. This is for controlling the pump 33.

By operating the brine circulation pump 33,
The cold heat of the ice stored in the brine in the heat storage tank 27 is led directly to the intake air cooler 20 by the brine supply pipe 25a,
In the intake air cooler 20, heat exchange with the intake air 21 is performed,
To cool. The brine whose temperature has increased due to the heat exchange is returned to the heat storage tank 27 via the brine return pipe 25b, and is cooled again. At this time, intake air temperature detector 29, intake air humidity detector
30, the signals output from the brine temperature detector 36 and the supply brine flow rate detector 37 are processed in the calculator 31, and the valve opening degree and the brine circulation pump in the brine flow rate control valve 26, The output of 33 is adjusted to control the amount of cold heat sent to the intake air cooler 20. At this time, by performing control so that the temperature of the intake air 21 after cooling becomes almost the dew point, it is possible to prevent the cool heat from being consumed as the condensation heat of the water contained in the intake air 21. Here, the flow rate control of the brine circulation pump 33 may be performed by controlling the number of revolutions by an inverter, or may be performed by controlling the number of pumps using a plurality of pumps. In addition, the intake air temperature detector 29 and the intake air humidity detector
30 may be installed at the intake inlet of intake cooler 20. In addition, the brine temperature detector 36 is placed one before and after the intake air cooler 20.
You may install two in total.

The amount of cold heat supplied to the intake air cooler 20 is controlled by using a brine circulation pump 33 as a constant flow pump.
It may be performed by adjusting the opening degree of the brine flow rate adjusting valve 26 and the auxiliary brine flow rate adjusting valve 35, or without providing the bypass pipe and the auxiliary brine flow rate adjusting valve 35,
The adjustment may be performed by adjusting the output of the brine circulation pump 33. With such a configuration, the cooling water is supplied using the stored cold heat, so that when the maximum output is required, the gas turbine intake air is consumed without consuming energy for producing the cooling water. Cooling can be performed efficiently, and a larger output can be generated even during the daytime in summer when load demand is highest. Further, by cooling the intake air using the cold stored in the form of ice, a sufficient intake air cooling effect can be exhibited even when the gas turbine is started. Further, in all the above configurations, fine-grained pure water can be sprayed further downstream of the intake air cooler 20. FIG. 5 is a diagram showing this configuration.
1 to 4 are denoted by the same reference numerals, and detailed description thereof will be omitted. In FIG. 5, the details of the intake air cooling device outside the intake passage 19 are the same as those shown in FIGS. 1 to 4 as the first embodiment, so that the illustration thereof is omitted.

As shown in FIG. 5, an intake filter 41 is provided downstream of the intake air cooler 20 installed in the intake passage 19, and a spray water supply pipe 43 is provided further downstream of the intake filter 41. Nozzle 42 for spraying pure water supplied from outside
Is installed. Pure water is sprayed from the spray nozzle 42 into the intake air 21 having passed through the intake air cooler 20 in a fine particle state. By spraying fine-grained pure water on the intake air 21 cooled by the intake air cooler 20, the mass flow rate of the intake air 21 can be further increased, so that the output can be further increased.
At this time, it can be further used as condensed drain water spray water generated by cooling the intake air 21 to the dew point or lower inside the intake air cooler 20. This configuration is shown in FIG.
1 to 5 are denoted by the same reference numerals, and the detailed description thereof will be omitted. Also, in FIG. 6, the details of the intake air cooling device outside the intake passage 19 are the same as those shown in FIGS. 1 to 4 as the first embodiment, so that the illustration thereof is omitted. In this configuration, in addition to the configuration described in FIG. 5, a drain recovery pipe 44 for recovering the condensed drain downstream of the intake air cooler 20 and a drain recovery tank 4
5. A spray water supply pipe for supplying pure water to the drain recovery tank 45 and a spray water pump 46 arranged in the middle of the spray water supply pipe 43 are provided.

With this configuration, the drain generated in the intake air cooler 20 is recovered by a drain recovery pipe 44, mixed with pure water supplied from the outside in a drain recovery tank 45, pressurized by a spray water pump 46, and then sprayed. I do. Thus, the intake air cooler 20
By using the condensed drain water generated inside, the drain water that has been conventionally discarded can be effectively used. In addition, since the condensed drain water is at substantially the same level as the temperature of the intake air 21 that has passed through the intake air cooler 20, it can be sprayed from the spray nozzle 42 at a lower temperature than when only pure water supplied from the outside is used. Therefore, it is possible to suppress a rise in the temperature of the intake air 21 to a low level.

[0019]

As described in detail above, using the cold energy stored during low load demand times such as at night, intake cooling is performed during the daytime in summer when load demand is maximized, and the mass flow rate of intake air is reduced. By increasing the value, an output can be obtained without loss, and a good intake air cooling effect can be obtained even at startup.

[Brief description of the drawings]

FIG. 1 is a system diagram showing a first embodiment of an intake air cooling device according to the present invention.

FIG. 2 is a system diagram showing a modified example of the first embodiment of the intake air cooling device according to the present invention.

FIG. 3 is a system diagram showing a modified example of the first embodiment of the intake air cooling device according to the present invention.

FIG. 4 is a system diagram showing a modified example of the first embodiment of the intake air cooling device according to the present invention.

FIG. 5 is a system diagram showing a cooling water spray device used in the first embodiment of the intake air cooling device according to the present invention.

FIG. 6 is a system diagram showing a modified example of the cooling water spray device used in the first embodiment of the intake air cooling device according to the present invention.

FIG. 7 is a system diagram showing a combined cycle power plant.

FIG. 8 is a diagram showing a relationship between an intake air temperature and an output in a combined cycle power plant.

FIG. 9 is a system diagram showing a combined cycle power plant incorporating a conventional intake air cooling device.

[Description of Signs] 1 ... Compressor 2 ... Combustor 3 ... Gas turbine 4 ... Exhaust heat recovery boiler 5 ... Steam turbine 6 ... Generator 7 ... Condenser 8 ... Condenser pump 19 ... Intake channel 20 ... Intake cooling Unit 21… Intake 22… Cooling water circulation system 22a… Cooling water supply piping 22b… Cooling water return piping 23… Cooling water flow control valve 24… Intermediate heat exchanger 25… Brine circulation system 25a… Brine supply piping 25b… Brine return piping 26 … Brine flow rate adjustment valve 27… Heat storage tank 28… Refrigerator 29… Intake air temperature meter 30… Intake hygrometer 31… Calculator 32… Cooling water circulation pump 33… Brine circulation pump 34… Auxiliary cooling water flow adjustment valve 35… Auxiliary brine flow rate Adjustment valve 36… Brine temperature detector 37… Brine flow detector 38… Cooling water flow detector 39… Cooling water temperature detector 41… Intake filter 42… Spray nozzle 43… Spray water supply pipe 44… Drain recovery pipe 45… Drain Recovery tank 46: spray water Pump 47 ... spray water supply piping

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Kiyohiko Kitagawa 2-4 Suehirocho, Tsurumi-ku, Yokohama, Kanagawa Prefecture Inside the Toshiba Keihin Plant (72) Inventor Katsuya Yamashita 2-4, Suehirocho, Tsurumi-ku, Yokohama-shi, Kanagawa (72) Inventor Mikio Takayanagi 1-1-1 Shibaura, Minato-ku, Tokyo In-house Toshiba Corporation (72) Inventor Yukio Shibuya 1-1-1 Shibaura, Minato-ku, Tokyo Toshiba Corporation In the office (72) Inventor Hiroshi Watanabe 1 Toshiba, Komukai Toshiba-cho, Saiwai-ku, Kawasaki-shi, Kanagawa Inside the Toshiba R & D Center

Claims (15)

[Claims] 1. A heat storage tank for storing ice produced by operating a refrigeration cycle as a cold heat source, and means for cooling intake air in an intake passage of a gas turbine compressor using the cold heat stored in the heat storage tank. An intake air cooling device for a gas turbine, comprising: 2. An intake air cooler installed in an intake air passage of a gas turbine compressor for cooling intake air by heat exchange with cooling water, a heat storage tank storing ice produced by operating a refrigeration cycle, and An intermediate heat exchanger is provided between the heat storage tank and the intake air cooler for exchanging heat with the cold stored in the heat storage tank and the cooling water.The intake air cooler and the intermediate heat exchanger transfer the cooling water. The cooling water circulation pump to be circulated, the cooling water supply pipe, and the cooling water return pipe are connected to form a cooling water circulation system, and the intermediate heat exchanger and the heat storage tank are liquids having a lower freezing point than water. An intake air cooling device for a gas turbine, which is connected via a brine circulating pump, a brine supply pipe, and a brine return pipe for circulating a certain brine to form a brine circulating system. 3. The intake cooling system for a gas turbine according to claim 2, wherein the brine circulating system includes a brine flow detector and a brine temperature detector, and is provided in the intake passage. A gas turbine having a processing unit for processing signals from an intake air temperature detector, an intake air humidity detector, the brine temperature detector, and the brine flow rate detector, and controlling the brine circulation pump. apparatus. 4. The intake cooling system for a gas turbine according to claim 2, wherein the brine circulating system includes a brine flow control valve, a brine bypass pipe that short-circuits the brine supply pipe and the brine return pipe, An auxiliary brine flow control valve provided in a brine bypass pipe, a brine flow detector, and a brine temperature detector are provided, and the intake air temperature detector, the intake humidity detector, and the brine provided in the intake passage are provided. Temperature detector,
And an arithmetic unit for processing a signal from the brine flow detector and controlling the brine flow control valve, the auxiliary brine flow control valve, and the brine circulation pump. 5. The intake cooling device for a gas turbine according to claim 4, wherein a constant flow type pump is used as the brine circulation pump. 6. The intake cooling system for a gas turbine according to claim 2, wherein the cooling water circulating system is provided with a cooling water flow rate detector and a cooling water temperature detector, and is provided in the intake flow path. A processing unit for processing a signal from the intake air temperature detector, the intake air humidity detector, the cooling water temperature detector, and the cooling water flow rate detector, and controlling the cooling water circulation pump. Turbine intake cooling system. 7. The cooling system according to claim 2, wherein the cooling water circulation system includes a cooling water flow control valve, and a cooling water bypass that short-circuits the cooling water supply pipe and the cooling water return pipe. A pipe, an auxiliary cooling water flow control valve provided in the cooling water bypass pipe, a cooling water flow detector, and a cooling water temperature detector, and an intake air temperature detector provided in the intake passage. Processing signals from the intake humidity detector, the cooling water temperature detector, and the cooling water flow detector to control the cooling water flow regulating valve, the auxiliary cooling water flow regulating valve, and the cooling water circulation pump. An intake air cooling device for a gas turbine, comprising an arithmetic unit. 8. The intake cooling system for a gas turbine according to claim 7, wherein a constant flow type pump is used as the cooling water circulation pump. 9. A gas turbine compressor comprising, in an intake passage, an intake air cooler for cooling intake air by heat exchange with cold heat, and a heat storage tank for storing ice produced by operating a refrigeration cycle as a cold heat source, A gas turbine, wherein the intake air cooler is connected to the heat storage tank via a brine circulating pump that circulates a brine having a freezing point lower than water, a brine supply pipe, and a brine return pipe, to form a brine circulating system. Intake cooling system. 10. The intake air cooling device for a gas turbine according to claim 9, wherein an intake air temperature detector and an intake air humidity detector provided in the intake air passage, and a brine temperature detector provided in the brine circulation system. A processing unit for processing a signal from a brine flow detector and controlling the brine circulation pump. 11. The intake cooling system for a gas turbine according to claim 9, wherein the brine circulating system includes a brine flow control valve, a brine bypass pipe that short-circuits the brine supply pipe and the brine return pipe, An auxiliary brine flow control valve provided in a brine bypass pipe, a brine flow detector, and a brine temperature detector are provided, and the intake air temperature detector, the intake humidity detector, and the brine provided in the intake passage are provided. A gas detector, comprising: a temperature detector, and a processor that processes a signal from the brine flow detector and controls the brine flow adjustment valve, the auxiliary brine flow adjustment valve, and the brine circulation pump. Inlet cooling device. 12. The intake cooling system for a gas turbine according to claim 11, wherein the brine circulation pump includes:
An intake cooling device for a gas turbine, wherein a constant flow type pump is used. 13. An intake cooling system for a gas turbine according to any one of claims 1 to 12, wherein: a means for cooling the intake air or a pure water supply means for supplying pure water to the downstream of the intake cooler from outside. An intake cooling device for a gas turbine, comprising: a spray nozzle that sprays supplied pure water into the intake passage downstream of the intake cooler in the form of fine particles. 14. The gas turbine intake cooling device according to claim 13, wherein a drain generated in the intake cooler is used as a part of the pure water. 15. The intake air cooling device according to claim 1, wherein the ice stored in the heat storage tank is:
A method for cooling an intake air of a gas turbine, comprising operating and manufacturing a refrigeration cycle using nighttime electric power.