JPH09177567A - Intake air cooling device for compressor, and method of operating it - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the cooling efficiency of the intake air cooling device of a gas turbine compressor. SOLUTION: A heat exchanger 5 for guiding a coolant from a refrigerating equipment 6 is provided within a cooling chamber 1 to which the intake air of a compressor 51 is introduced. The heat exchanger 5 is dipped in water in the night to make ice. In generation in the daytime, water is drained, and intake air is directly cooled by the exposed ice. In this case, the intake quantity carried in a bypass duct 4 is regulated by a damper V1 to control the intake air temperature in the inlet of the compressor 51.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a structure of an intake air cooling device for a gas turbine compressor and a method of operating the same.

[0002]

2. Description of the Related Art FIG. 17 is a system diagram showing an example of a conventional intake cooling system for a gas turbine compressor. The intake air of the gas turbine compressor (51) is taken in from the intake chamber (52) and reaches the intake port of the compressor (51) through the intake duct (53).

An intake air cooling heat exchanger (54) is installed in the middle of the intake duct (53) to cool the intake air.
The cooling medium of the heat exchanger (54) is a cold water tank (5
It is the cold water stored in 5).

Cold water is produced mainly at night. In that case, the refrigerating equipment (56) is operated to circulate the refrigerant in the cooling heat exchanger (57), and a sherbet liquid of ice and water is stored in the cold water tank (55). Then, during the daytime operation of the gas turbine, cold water is taken out by the cold water pump (58) and sent to the intake air cooling heat exchanger (54) to cool the intake air, and then returned to the cold water tank (55).

[0005]

The above-mentioned conventional intake air cooling system has the following problems to be solved. That is, since cold water is circulated and heat is indirectly exchanged in the intake air cooling heat exchanger (54), the cooling efficiency is poor. Since the cold water is kept at a temperature of about 0 ° C. to 10 ° C. in consideration of fluidity and the like, the cooling effect is not improved.

Further, when the intake air is cooled, the water content of the intake air is condensed to form water drops or mist, which easily flows into the compressor (51).

Further structurally, the heat exchanger for cooling the intake air (5
4) and a cooling heat exchanger (57) are required.

[0008]

In order to solve the above-mentioned conventional problems, the inventor of the present invention is provided in the middle of an intake duct from the intake chamber to the inlet of the gas turbine compressor, and the cooling heat exchanger is installed in the lower part thereof. A cooling chamber for accommodating a heat pipe, a refrigeration facility connected to the refrigerant inlet / outlet of the heat transfer pipe, a bypass duct communicating with the intake / outlet inlet / outlet of the cooling chamber and having a temperature control damper, and an intake air introduced into the cooling chamber An injection nozzle for injecting cold water into the cold water, a cold water pipe from the bottom of the cooling chamber to the cold water tank via a cold water transfer pump and a liquid level control valve, and a cold water injection pump from the cold water tank and a cold water injection control valve A cold water injection pipe for supplying cold water to the injection nozzle; and a water injection pipe branching from the outlet of the cold water injection pump to communicate with the cooling chamber and having a water injection control valve. The compressor intake air cooling system is provided, and water is poured into the cooling chamber at night, and ice is generated and adheres to the heat transfer tube surface of the cooling heat exchanger by using the nighttime electric power. Lower it to expose the ice on the heat transfer tube surface, and directly contact the intake air with the ice surface to cool the intake air,
In addition, even when ice is being made with night power, power generation and intake cooling can be performed if necessary.

Further, according to the present invention, the refrigerating equipment is a turbo refrigerator using a refrigerant such as CFC gas or ammonia, LNG.
Carburetor, constitute _{air, N 2, O 2, CO} 2 , etc. liquefaction equipment, or liquid air, liquid N _2, a liquid O _2, in at least one of the vaporization equipment such as liquid CO _2, also, the The cooling heat exchanger provides an intake air cooling device for a compressor having a heder structure in which a large number of cooling pipes are forested.Each equipment below the turbo refrigerator is a liquefied gas, and when it is vaporized, it is vaporized. It takes latent heat and cools the cooling pipes standing in the header of the cooling heat exchanger. The vaporized gas is circulated again to the refrigerator of the refrigeration facility in the case of CFC gas, and is fed to the gas turbine fuel when the refrigeration facility is LNG gas, for example. In the case of liquid air vaporization equipment, the vaporized air mixes with the intake air to enhance cooling. In the case of liquid nitrogen, liquid oxygen and liquid carbon dioxide gas, the vaporized nitrogen, oxygen and carbon dioxide gas are put into the corresponding system of the combined power generation system.

According to the present invention, the temperature control damper is
A single-valve or multi-valve structure is provided on the inlet side of the bypass duct, and an intake air cooling device for the compressor is also provided on the outlet side of the bypass duct to provide a cooling system for the intake side of the bypass duct. By making the adjustment damper a multi-looper damper, for example,
The bypass flow that flows through the bypass duct is rectified and fine control becomes possible. Further, by installing a damper also on the outlet side of the bypass duct, turbulent flow in the duct is rectified, and the problem of vibration of the bypass duct is solved in synergy with the effect of the multi-loop damper.

The present invention also provides an intake air cooling device for a compressor, in which the cold water tank is disposed at the bottom of the cooling chamber and integrated with the cooling chamber, and the bottom surface of the cooling chamber is inclined. Since the chamber and the cold water tank are integrated with each other, the attached control valves can be attached inside the cold water tank or on the side wall of the tank, whereby the equipment can be prevented from being arranged on a flat surface and the size can be reduced. Further, by changing the structure of the cold water tank, the flow of cold water and air in the tank can be made smooth, and the drain of the drain can be ensured due to the inclination of the bottom of the cooling chamber.

Further, the present invention provides an intake air cooling device for a compressor, wherein a dehumidifier is installed in a duct from the bypass duct outlet to the intake port of the gas turbine compressor or at the intake outlet of the cooling heat exchanger. However, by installing a dehumidifier such as a mist separator, dehumidification of intake air is thorough,
There is no inflow of moisture into the gas turbine compressor.

Further, the present invention is based on the intake air temperature and intake pressure at the gas turbine compressor inlet and the gas turbine output, the temperature adjusting damper, the liquid level control valve,
Provided is a method for operating an intake air cooling device of a compressor, which controls the cold water injection control valve and / or the water injection control valve to raise and lower the water level in the cooling chamber to adjust the temperature of intake air.
During the night, water is poured into the cooling chamber and the night power is used to generate and adhere ice to the heat transfer tube surface of the cooling heat exchanger, and during daytime power generation, the water level in the cooling chamber is lowered to expose the ice on the heat transfer tube surface. This is a method of operation that allows the intake air to be cooled by direct contact between the intake air and the ice surface, and also to generate power and cool the intake air when necessary even when ice is being produced by night-time power.

[0014]

DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 is a system diagram showing an intake air cooling system for a gas turbine compressor according to an embodiment of the present invention.

Reference numeral (1) is a cooling chamber, which is provided in the middle of an intake duct (3) from the intake chamber (2) to the inlet of the gas turbine compressor (51), and has a cooling heat exchanger (5) in the lower part. Housing the heat transfer tubes. (6) is a refrigerating facility connected to the refrigerant inlet / outlet of the heat transfer tube.

A horizontal partition plate (4) is provided above the cooling chamber (1).
a) is provided, and a bypass duct (4) which communicates the intake inlet and the intake outlet of the cooling chamber is formed above it. A temperature adjusting damper (V1) is provided on the inlet side of the bypass duct (4).

Outside the cooling chamber (1) is a cold water tank (7).
Is installed and communicates with the bottom of the cooling chamber (1) through the cold water pipe (8). Then, a chilled water transfer pump (9) and a liquid level control valve (V
2) is provided. Further, a cold water injection pipe (11) for supplying cold water from the cold water tank (7) is arranged to the injection nozzle (10) in the intake duct (3), and a cold water injection pump (11) is provided in the cold water injection pipe (11). 12) and a cold water injection control valve (V3) are provided. Furthermore, cold water injection pump (1
A water injection pipe (13) that branches from the outlet side of 2) and communicates with the cooling chamber (1) is provided, and a water injection control valve (V
4) is provided.

The temperature and pressure (1
The detection signals of 4) and (15) and the gas turbine power generation output signal are input to the intake air temperature control device (16), and the output signal outputs the damper (V) for adjusting the temperature of the bypass duct (4).
1), while controlling the liquid level control valve (V2) of the cold water pipe (8), the cold water injection control valve (V3) of the cold water injection pipe (11) and the water injection control valve (V4) of the water injection pipe (13) ,
In addition to the above-mentioned temperature adjustment, the pressure adjustment for setting the intake pressure (15) to a predetermined value can be combined and controlled. Reference numeral (17) is a liquid level transmitter that controls the liquid level control valve (V2).

In the intake air cooling device of this embodiment, water is poured into the cooling chamber (1) at night to immerse the heat transfer tube of the cooling heat exchanger (5), and ice is applied to the surface of the heat transfer tube by using night power. Is generated and attached. During daytime power generation, the water level in the cooling chamber (1) is lowered to expose the ice on the heat transfer tube surface, and the intake air and the ice surface are brought into direct contact to cool the intake air. Moreover, even when ice is being made with night power, power generation and intake air cooling are possible if necessary.

Next, as shown in FIG. 2, the operation of the cooling chamber can correspond to a non-cooling mode (ice making mode), a full cooling mode and a half cooling mode.

(A) In the non-cooling mode (ice making mode), the temperature control damper (V1) is fully opened and the liquid level in the cooling chamber (1) is full of water for ice making. When operating the gas turbine during ice making, intake air is sent to the compressor (51) via the bypass duct (4). In this case, the intake air is simply sucked into the atmosphere, and the intake air is not cooled.

(B) In the total cooling mode (when maximum cooling performance is desired), the temperature control damper (V1) is fully closed, the liquid level in the cooling chamber (1) is at the lowest level, and the total amount of intake air is ice. Contact them for heat exchange.

(C) In the semi-cooling mode (when desired cooling performance is desired), the temperature control damper (V1) is semi-open, and the liquid level in the cooling chamber (1) is at the middle water level. In this case, the ice of the cooling heat exchanger (5) is partially exposed, and the cooling heat exchanger (5) is
The temperature control damper (V1) controls the ratio of the intake air cooled by (4) and the intake air flowing through the bypass duct (4) without being cooled.

The temperature adjusting operation is performed by the compressor (51).
The temperature / pressure signals (14) and (15) of the intake port of the engine and the gas turbine power generation output signal are input to the intake temperature control device (16), and the temperature control damper (V1) is output by the output signal.
(Bypass control), Liquid level control valve (V2) (Ice exposure control)
The cold water injection control valve (V3) (cold water injection control) is controlled. Further, the intake pressure is controlled and adjusted by being combined (superposed) with the temperature adjustment.

In the present embodiment, the condensed water is collected on the ice surface, partly freezes, and partly flows down to the water surface below. Further, as for the water content toward the gas turbine intake port in the ascending flow, the coarse particles drop by gravity, and the fine particle water also mixes with the high temperature intake air that has passed through the bypass duct (4), so that the dryness increases.
Mist and water drops flowing into the compressor are reduced.

Table 1 shows this embodiment in comparison with the prior art.

[0027]

[Table 1]

In the present embodiment, various modifications and alterations can be made to the cooling heat exchanger, the bypass duct, the cold water tank, the refrigerating equipment, and the like, which are attached thereto. An example will be described.

3 to 7 show a modification of the cooling heat exchanger, which is not shown in detail in FIG. 3, but the refrigerating equipment (6).
CFC-based refrigerator, LNG vaporizer, and air,
A liquefaction facility or a vaporization facility that handles a liquefied gas such as nitrogen, oxygen, and carbon dioxide is assumed, and the cooling heat exchanger (5) in the cooling chamber (1) has an upper head (5B).
And a lower header (5A) are arranged, and a large number of cooling pipes (5C) are provided so as to communicate between the both headers.

The refrigerant liquid flows from the refrigeration equipment (6) through the refrigerant liquid pump (28) and the control valve (V5) to the lower header (5).
A), the cooling pipe (5C) removes the latent heat of vaporization from the intake air flowing in the direction of the arrow to vaporize it, and the upper header (5)
From B), LNG gas is sent to a gas turbine (not shown), vaporized air is sent to the next process, and CFC vapor is sent to the refrigeration equipment (6). In addition, the code | symbol (29) is a heat insulating material here.

FIG. 4 is a partially modified version of the one shown in FIG. 3, and FIG. 4 (a) shows the front surface, and FIG. 4 (b) shows the side surface.
A plurality of lower headers (5A) are provided to lengthen the entire length of the cooling pipe (5C) to improve heat exchange performance.

FIG. 5 assumes the case where liquefied air is used as the refrigeration equipment (6), and the vaporized component of the liquefied air is
The structure itself can mix with air to enhance the cooling function. That is, ice is generated in the (C1) portion of the cooling pipe (5C) and mixed with the intake air in the (C2) portion. Where (C
The boundary between 1) and (C2), that is, the division of the (C1) region and the (C2) region is performed by the liquid level controller LC and the control valve (V5).

In FIG. 6, vaporized air is introduced into the bypass duct 4 to cool the bypass duct 4 together with the cooling chamber 1. Here, various shapes of the cooling pipe 5C can be selected, some of which are shown in FIGS. 7 (a) to 7 (e-2).

That is, FIG. 7A shows that the upper end is cut horizontally to form an opening to form a flow of vaporized air that is orthogonal to the flow in the bypass duct (4). In b), the upper end is cut along a slope facing the downstream direction to form an opening, and a flow of vaporized air is formed along the flow in the bypass duct (4) as much as possible. An upper end is cut horizontally to form an opening, and a notch that extends partway in the longitudinal direction is formed on the wake side to form a flow of vaporized air that is a combination of (a) and (b). 7 (d) is different from that of FIG. 7 (c) in that the upper end is covered and only the notch extending halfway in the longitudinal direction is formed on the wake side to form the inside of the bypass duct (4). To form a flow of vaporized air as closely as possible to the flow of Of (e-1) FIG. 7
Although it is similar to (d) of FIG.
-2) As shown in Fig. 2), a part of the tip is inflated in the front-back direction of the flow, and on the other hand, it is narrowed in the width direction at a right angle to this, and vaporization along the flow in the bypass duct (4) is endless. It is designed to form a flow of air.

In FIG. 8, the temperature control damper (V1 _a ) attached to the inlet side of the bypass duct (4) is a single valve or a multi-valve (multi-looper damper), and the outlet side of the bypass duct (4) is also provided with a separate valve. A temperature control damper (V1 _b ) is attached to adjust the bypass flow to enable fine control, and the problem of vibration of the bypass duct (4) due to turbulent flow in the bypass duct (4) is also solved.

In FIG. 9, a cold water tank (7) is arranged adjacent to the bottom of the cooling chamber (1), and both are combined to form an integrated structure. The cooling chamber (1) and the cold water tank (7)
Piping (7A) that communicates with (cold water piping, water input piping,
Cold water injection pipes, etc. correspond to this), the cold water tank (7)
It is mounted inside or on the side wall of the cold water tank (7) to make the whole compact.

FIG. 10 shows the ceiling portion (7) of the cold water tank (7).
B) (corresponding to the bottom of the cooling chamber (1)) and the bottom (7C) are inclined to make the flow of cold water at the bottom smooth. A cold water pool pit (7D) is further provided at the bottom (7C). Further, an intake / inlet pipe (7E) communicating with the cooling chamber (1) is attached to the ceiling portion (7B) of the cold water tank (7), and through the pit (7D) as water in and goes out of the lower tank. Entry and exit of air is secured.

In FIG. 11, a dehumidifier (mist separator) (20) is attached to a duct (3A) extending from the outlet of the bypass duct (4) to the intake port of a gas turbine compressor (not shown). This is to prevent unnecessary moisture from being supplied to the downstream gas turbine compressor or the like.

FIG. 12 also shows a dehumidifier (mist separator) (2
0) is attached, but this is different from the installation position of the one shown in FIG. 11 described above in that the dehumidifier (20) is attached to the intake / outlet portion of the cooling heat exchanger (5), and the cooling heat exchange is exclusively performed. The moisture from the container (5) side is removed.

FIG. 13 shows a refrigerating heat source which is devised so that the refrigerating machine (6A) and the LNG vaporizing equipment (6A) are used as the cold heat source.
B), and a plurality of cold heat source equipments of liquid air equipment (6C), and each cold heat source equipment can be replaced and used by switching. In this case, the switching control is performed by the signal from the temperature detector TC of the refrigerant tank (6G), and the refrigerant heat exchanger (6D) corresponding to each cold heat source,
(6E), (6F) and the control valves (V4H), (V4I), and (V4J) corresponding to the respective refrigerant heat exchangers are controlled.

FIG. 14 shows that the cooling heat exchanger 5 is divided into an LNG vaporization facility (6A), a refrigerator facility (6B), and a liquid air facility (6C) for each cold heat source, and these are independently cooled. Heat exchanger (5A), (5B), (5C)
If necessary, switching control is performed by a switching device (not shown), and a combination of cooling heat exchangers with different cooling heat sources is used to operate in each temperature range t ₁ , t ₂ , t _i. The inlet side temperature T ₁ can be adjusted to the outlet side temperature T ₂ .

In FIGS. 15 and 16, the change in operating environment when the cold heat source is switched and used as shown in FIGS. 13 and 14 is divided into nighttime (FIG. 15) and daytime (FIG. 16). Show. That is, the LNG vaporization equipment (4A) of the cold heat source
(LNG cold heat), refrigerator equipment (4B) (turbo refrigerator), and liquid air equipment (4C) (air liquefaction) are generally LNG cold heat (power 0) <
Since there is a relationship of turbo chiller << air liquefaction, the electric turbo chiller is first operated by the difference between the base output and the demand (excess electric power), and then air liquefaction is performed.

When the stored ice cold heat is used as the cold heat source, there is a relationship of LNG cold heat and stored ice cold heat (power 0) <turbo refrigerator, so that the portion that is insufficient in the stored ice cold heat is consumed by the turbo refrigerator. For the amount of the auxiliary heat that frequently changes the cold heat, it is advisable to use the heat storage liquid air with good control response for charging and cooling.

Furthermore, in FIGS.
Is heat storage ice cold heat, B is an electric turbo refrigerator, C is heat storage liquid air, or LNG vaporized cold heat, is electric turbo cold heat, and is air liquefied cold heat.

Although the present invention has been described with reference to the illustrated embodiment, the present invention is not limited to such an embodiment.
It goes without saying that various modifications may be made to the specific structure within the scope of the present invention.

[0046]

According to the present invention, the following effects can be obtained. 1) Since the intake air is in direct contact with the ice, the intake air can be cooled to near 0 ° C. 2) The water condensed by cooling the intake air adheres to the ice surface or is collected on the water surface of the cooling chamber, so that the amount of water flowing into the gas turbine can be reduced. 3) Electricity is leveled when ice is made with nighttime electricity. 4) The temperature of the intake air can be freely adjusted by using the cooling heat exchanger and the bypass duct together. 5) The intake air can be cooled only by the cooling heat exchanger. 6) The cold water stored in the cold water tank by adjusting the temperature can also be used as cooling water for other coolers. 7) By making various modifications to the cooling heat exchanger, bypass duct, cold water tank, refrigeration equipment, etc., specificity and precision are added to the overall function and operation, which greatly contributes to improving the function of the intake air cooling system. It is a thing.

[Brief description of the drawings]

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

FIG. 2 is a diagram showing an operation mode of the above embodiment.

FIG. 3 is a conceptual diagram showing a specific example of a cooling heat exchanger.

FIG. 4 is a conceptual view showing another specific example of the cooling heat exchanger, (a) is a front view and (b) is a side view.

FIG. 5 is a conceptual diagram showing still another specific example of the cooling heat exchanger.

FIG. 6 is a conceptual diagram showing still another specific example of the cooling heat exchanger.

7 is a perspective view of a cooling pipe which is a main part of FIG.
(A), (b), (c), (d), (e-1) and (e-2) showing the plane of the same (e-1) are classified into (e-2) to show various modifications of the cooling pipe. It is a schematic diagram.

FIG. 8 is a structural conceptual diagram of a bypass duct showing an example in which the bypass duct is modified.

FIG. 9 is a structural conceptual diagram of a cooling chamber and a cold water tank that are integrally structured.

10 is a structural conceptual diagram showing another example different from FIG. 9 in which the cooling chamber and the cold water tank are integrally structured as in FIG. 9.

FIG. 11 is a mounting structure diagram of a dehumidifier showing an example in which a dehumidifier is incorporated in a cooling heat exchanger.

FIG. 12 is a mounting structure diagram of a dehumidifier in which a dehumidifier is incorporated in a cooling heat exchanger as in the case of FIG. 11, and another example different from FIG. 11 is shown.

FIG. 13 is a system diagram of a refrigerating facility showing an example in which a plurality of refrigerating facilities are provided side by side.

FIG. 14 is a system diagram of refrigerating equipment in which a plurality of refrigerating equipments are arranged similarly to FIG. 13 and showing another example different from FIG.

FIG. 15 is an explanatory diagram for explaining an operating environment at night in a plurality of facilities as shown in FIGS. 13 and 14, (a) showing a power demand situation, and (b) showing a power consumption situation. FIG.

FIG. 16 is an explanatory diagram illustrating a daytime situation, whereas FIG. 15 shows nighttime.

FIG. 17 is a system diagram showing an example of a conventional intake-air cooling device for a gas turbine compressor.

[Explanation of symbols]

 (1) Cooling chamber (2) Intake chamber (3) Intake duct (4) Bypass duct (4a) Partition plate (5) Cooling heat exchanger (5A) Lower head (5B) Upper head (5C) Cooling pipe (6) Refrigeration equipment (6A) LNG vaporization equipment (6B) Refrigeration equipment (6C) Liquid air equipment (6D) Refrigerant heat exchanger (6E) Refrigerant heat exchanger (6F) Refrigerant heat exchanger (6G) Refrigerant tank (7) Cold water Tank (7A) Pipes (7B) Ceiling (7C) Bottom (7D) Water supply pit (7E) Intake / outlet pipe (8) Cold water pipe (9) Cold water transfer pump (10) Cold water injection nozzle (11) Cold water injection pipe (12) Cold water injection pump (13) Water injection pipe (14) Temperature detector (15) Pressure detector (16) Intake air temperature control device (20) Dehumidifier (28) Refrigerant liquid pump (29) Insulating material (51) Gas turbine compressor (52) Intake chamber (53) Intake pipe (54) Intake cooling heat exchanger (55) Cold water tank (56) Refrigeration equipment (57) Cooling heat exchanger (58) Cold water pump (V1) Temperature control Damper (V2) Liquid level control valve (V3) Cold water injection control valve (V4) Water injection control valve (V5) Control valve (V4H) Control valve (V4I) Control valve (V4J) Control valve

Claims (7)

[Claims] 1. A cooling chamber which is provided in the middle of an intake duct from an intake chamber to a gas turbine compressor inlet, and which accommodates a heat transfer tube of a cooling heat exchanger at a lower portion thereof, and a refrigeration connected to a refrigerant inlet / outlet of the heat transfer tube. A facility, a bypass duct that communicates the inlet and outlet ports of the cooling chamber with each other and has a temperature control damper, an injection nozzle that injects cold water into the intake air introduced into the cooling chamber, a cold water transfer pump from the bottom of the cooling chamber, and Cold water piping to the cold water tank through the liquid level control valve, cold water injection piping for supplying cold water from the cold water tank to the injection nozzle via the cold water injection pump and the cold water injection control valve, and from the outlet of the cold water injection pump An intake air cooling device for a compressor, comprising: a water injection pipe having a water injection control valve, the water intake pipe being branched and connected to the cooling chamber. 2. The refrigerating facility is a turbo refrigerator using a refrigerant such as CFC gas, ammonia, LNG vaporizer, air, liquefying facility such as N ₂ , O _2, CO ₂ , or liquid air, liquid N ₂ , liquid. O _2, constituted by at least one of the vaporization equipment such as liquid CO _2, also, the cooling heat exchanger according to claim 1, characterized in that a Heda structure bristled a plurality of cooling tubes Compressor air intake cooling system. 3. The temperature control damper having a single-valve or multi-valve structure is provided on the inlet side of the bypass duct, and the temperature control damper is also provided on the outlet side of the bypass duct. Alternatively, the intake air cooling device of the compressor according to the item 2. 4. The cold water tank is disposed at a bottom portion of the cooling chamber to have an integral structure with the cooling chamber, and the bottom surface of the cooling chamber is inclined. Compressor air intake cooling system. 5. A dehumidifier is installed in the duct extending from the outlet of the bypass duct to the intake port of the gas turbine compressor or at the intake outlet of the cooling heat exchanger. The intake air cooling device for a compressor according to 3 or 4. 6. The turbo refrigerator using the CFC gas, refrigerant, such as ammonia, LNG vaporizers, air, N _2, O _2, C
The refrigerating equipment composed of liquefying equipment such as O ₂ or vaporizing equipment such as liquid air, liquid N ₂ , liquid O _2, liquid CO ₂ is a switching valve, or a refrigerant pipe corresponding to each equipment is the cooling heat exchanger. The intake air cooling device for a compressor according to claim 1, 2, 3, 4, or 5, which is provided inside and is operable for each facility. 7. Based on the intake temperature and intake pressure at the gas turbine compressor inlet and the gas turbine output,
The temperature control damper, the liquid level control valve, the cold water injection control valve and / or the water injection control valve are controlled to raise or lower the water level in the cooling chamber to adjust the temperature of the intake air. Item 7. A method of operating an intake air cooling device for a compressor according to item 1, 2, 3, 4, 5 or 6.