JPH08144785A - Gas turbine intake cooling device - Google Patents

Abstract

PURPOSE: To increase the output of a gas turbine with good efficiency with small pressure loss on the air side. CONSTITUTION: An intake duct for forming an intake passage of air for combustion of a gas turbine is made diverge into two parts, a passage switching damper 2 is disposed in the diverging part, plural cooling plates 4 are vertically installed at suitable spaces in such a manner as to be parallel to the flow direction of intake air in one diverged intake duct 1a and form a hollow part in the interior thereof by two flat plates, and an ice heat storage reservoir 6 including a water supply part and an ice heat storage part is provided on the upper surface of the diverged intake duct 1a in such a manner as to communicate from the upper side of each cooling plate 4 to the hollow part. Accordingly, water which flows down from the water supply part of the ice heat storage reservoir 6 through the ice heat storage part is introduced into the hollow part of each cooling plate 4 and evaporated in high vacuum condition by the intake air of the gas turbine.

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 air cooling device capable of coping with an increase in output of gas turbine equipment of a combined cycle power plant.

[0002]

2. Description of the Related Art In recent years, in thermal power generation facilities, a single cycle power generation plant is being replaced with a combined cycle power generation plant capable of improving thermal efficiency when the old cycle is replaced.

Unlike the single cycle power plant, this combined cycle power plant is equipped with a gas turbine instead of the conventional boiler, and a generator driven by this gas turbine and exhaust heat utilizing the exhaust gas of the gas turbine are used. Power is generated by a steam turbine-driven generator that is supplied with steam from a recovery boiler, and the efficiency is 10% compared to a single-cycle power plant.
It is improved by about%. A gas turbine used in this combined cycle power generation plant supplies high-temperature and high-pressure gas by supplying compressed air to fuel and burning it, and the turbine is rotated by the gas to obtain power.

The output of this gas turbine is affected by the temperature and humidity of the combustion air. Further, the gas turbine is related to the inhalable oxygen amount (air amount), and increases as the intake air amount increases and as the temperature becomes lower.

In this case, the more moisture in the air, the greater the amount of water vapor in the high pressure / high temperature gas, and the amount of latent heat of this water vapor is discharged to the outside without being used even after being cooled by the exhaust heat recovery boiler. Therefore, the output of combined cycle power generation can be increased when the water content (humidity) in the intake air is smaller.

Therefore, the output characteristics are different in summer and winter, and especially during the daytime in summer, when the power demand reaches a peak, the output reduction of this combined cycle power generation is a serious problem.

[0007]

The gas turbine intake air cooling system that has been proposed at present utilizes ice heat storage, and the cold heat is stored in the form of ice by a refrigerator during low power demand at night, and is used during the daytime. This cold heat is taken out at the peak of, and the intake air of the gas turbine is cooled. That is, the refrigerator is operated by using seawater as cooling water at night to store ice in the ice heat storage tank, and the cold water thawed at the peak of daytime is used to cool the air with a heat exchanger (air cooler: intake passage). It is installed inside) to cool the intake air of the gas turbine.

[0008] In this system, there is a problem in the amount of ice stored in the ice heat storage tank. If the ice storage capacity is small, the ice heat storage tank itself becomes large, and there are two major large-scale components, a refrigerator and an air cooler. Therefore, it is difficult to put it into practical use in terms of cost and space.

Further, a technical problem in the ice heat storage tank of this system is that after the ice is made during the peak hours of the daytime (about 18 hours), the cold heat is removed in about 2 to 4 hours during the peak hours of the daytime. It is due to taking out. In other words, the necessity of melting the ice at a high speed and the fact that the temperature of the return water from the air cooler cannot be made too high make the chilled water circulation amount between the ice storage tank and the air cooler extremely large, and It is about 4 to 6 times as large as the large-scale ice heat storage system for air conditioning.

Further, when the circulation flow rate of the cold water increases, the convection time of the return water in the ice heat storage tank is short, and the ice water is circulated without being sufficiently melted. Therefore, the intake temperature of the cold water becomes high, and the size of the air cooler for passing the cold water through the pipe to exchange heat with the air becomes large. Then, the pressure loss on the air side when passing through the air cooler increases, and the pressure drops, which causes a problem of reducing the intake oxygen amount.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a gas turbine intake air cooling device which has a small pressure loss on the air side and which can efficiently increase the output of a gas turbine. To do.

[0012]

In order to achieve the above-mentioned object, the present invention comprises a gas turbine intake air cooling device by the following means. In the invention corresponding to claim 1, the intake duct forming the intake passage of the combustion air of the gas turbine is branched into two, and a passage switching damper is provided at the branch portion, and one of the branch intake ducts is provided. A plurality of cooling plates, each of which has a hollow portion formed by two flat plates inside, are vertically installed at appropriate intervals so as to be parallel to the flow direction of the intake air, and the upper part of each cooling plate. The cold water is guided to the hollow portion so as to be evaporated by the intake air of the gas turbine.

According to a second aspect of the present invention, an intake duct forming a suction flow path for combustion air of a gas turbine is branched into two parts, and a flow path switching damper is provided at the branch part. A plurality of cooling plates, each having a hollow portion formed by two flat plates inside the duct, are installed vertically at appropriate intervals so as to be parallel to the flow direction of the intake air. An ice heat storage container having a water supply unit and an ice heat storage unit on the upper surface is provided so as to communicate with the hollow portion from the upper portion of each cooling plate, and water flowing down from the water supply unit of the ice heat storage container through the ice heat storage unit. Is introduced into the hollow portion of each cooling plate to be evaporated in a high vacuum state by the intake of the gas turbine.

According to a third aspect of the present invention, as an ice heat storage part of the ice heat storage container of the second aspect of the invention, the ice storage part is provided at the upper and side portions, respectively, and the temperature is 0 ° C. or less which is passed from the refrigerator. A group of horizontal heat transfer tubes to which static ice is adhered by brine, and water distributors which are respectively arranged on the uppermost side, upper side and middle side, and which supply water to the outer surfaces of the horizontal heat transfer tube groups from the upper side. It is designed to be configured.

The invention according to claim 4 is a water distributor arranged laterally of the intermediate portion of the ice heat storage container of the invention as claimed in claim 3, which is a horizontal pipe group having holes at the bottom thereof. The groups are arranged diagonally and the upper part is fixed by a flat plate.

The invention corresponding to claim 5 is the cooling plate of the invention according to claim 1 or 2, and is 10 with respect to a horizontal plane.
A gutter-shaped beam tilted more than a degree is provided so as to be sandwiched between two flat plates.

The invention corresponding to claim 6 is such that the two flat plates constituting the cooling plate of the invention according to claim 1 or 2 are made into a porous surface by copper spraying on the inner wall through which water flows down, and The outer wall for heat exchange is provided with vertical ribs at regular intervals based on the horizontal groove.

[0018]

In the gas turbine intake air cooling device of the invention corresponding to claim 1, the intake duct serving as the intake passage of the gas turbine is branched into two, and one of the branched intake ducts is provided with a cooling section. The other branch intake duct is limited to space, and by using a flow path switching damper, an intake duct without a cooling unit is used at night, and an intake duct with a cooling unit is used during the daytime to lower the intake temperature, thus It is possible to increase the output of the gas turbine during peak power loads. And the cooling plate that cools the intake air is hollow,
By allowing water to flow down and evaporate in a high vacuum state, it is possible to cool intake air with a low heat transfer area and low pressure loss.

In the gas turbine intake air cooling device of the invention corresponding to claim 2, in addition to the above-mentioned function and effect, water is evaporated from the hollow portion of the cooling plate in a high vacuum state. It is possible to condense and absorb water vapor on the ice surface of the ice heat storage part in the ice heat storage container provided with the water supply part and the ice heat storage part provided on the upper surface so as to communicate with the hollow part from the upper part of each cooling plate. Become.

In the gas turbine intake air cooling device of the invention according to claim 3, in addition to the effect of the invention of claim 2, it is possible to smoothly supply water vapor to the ice surface.

In the gas turbine intake air cooling device of the invention according to claim 4, static ice can be generated in a falling liquid film state by flowing down water from the water distributor for ice making in a high vacuum state, and ice storage. Since the water distributor on the side of the middle part of the container also serves as a falling water trapping plate, water generated by condensation of water vapor and melting of surface ice covers the ice surface at the time of thawing ice, thereby preventing deterioration of water vapor condensation performance.

In the gas turbine intake air cooling device of the invention corresponding to claim 5, the thin plate of the vertical cooling plate and the gutter-shaped beam are used to improve the evaporative performance of the falling liquid film in the hollow portion. be able to.

In the gas turbine intake air cooling device of the invention according to claim 6, the inner wall of the flat plate for exchanging heat between water and intake air is made porous, and the outer wall is made up of horizontal grooves and vertical ribs. Therefore, it is possible to efficiently cool the intake air without scattering the water in the air.

[0024]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a perspective view showing a configuration example of a gas turbine intake air cooling device according to the present invention, and FIG. 2 is a view of the gas turbine intake air cooling device seen from the intake side. In FIG. 1 and FIG. 2, the gas turbine intake duct 1 is branched into two, a branch intake duct 1a having a cooling part and a branch intake duct 1b not having a cooling part, and a branch part between these branch intake ducts 1a and 1b. Is provided with a flow path switching damper 2.

The cooling unit includes a plurality of air cooling panels (vertical cooling plates) 4 vertically provided at equal intervals in the branch intake duct 1a and a water intake plate 7 disposed at the bottom.
And an ice heat storage container 6 provided in an opening on the upper surface of the branch intake duct 1a, in which an ice adhesion pipe group 5 is arranged, and water is drawn from the water intake plate 7 and the bottom of the ice heat storage container 6 to attach ice. A water circulating water pump 28 for supplying water from above the pipe group 5 is provided.

As shown in FIGS. 3 and 4, the vertical cooling plate 4 is constructed by sandwiching a gutter-shaped beam 23 inclined between the flat plates 4a and 4b at an angle of 10 degrees or more with respect to the flat plate, as shown in FIG. As shown in Fig. 2, the connection between the gutter-shaped beam 23 and the flat plate is widened toward the end.
It is set to 4. A porous chamber surface 25 is formed on the inner wall of the flat plate through which the water 22 flows down by copper spraying.

Further, as shown in FIG. 6, the vertical cooling plate 4 is formed with the horizontal grooves 26, the vertical ribs 27 are fixed at regular intervals, and the ice storage container 6 is projected from the upper surface 19 of the branch intake duct 1a. Fixed to the upper part 20 of the vertical cooling plate 4.
Is provided with a notch 21 for supplying water 22 to the inner wall thereof, and the Fluorinert type water level controller 11 shown in FIG.
The flow rate is kept constant by.

Further, the ice heat storage container 6 has a large number of horizontal heat transfer pipes 5 (ice adhesion pipes) for adhering and storing ice outside the pipes. The horizontal heat transfer pipes 5a in the upper part and the horizontal heat transfer pipes 5b in the side parts are provided. I know.

A water distributor 8 for supplying water to the horizontal heat transfer tube group 5 is provided. The water distributor 8 includes an uppermost water distributor 8a for supplying water to the upper heat transfer tube group 5a and an upper side water distributor 8b for supplying water to the side heat transfer tube group 5b and a side heat transfer tube group 5b. It is provided with a water distributor 8c on the side of the middle part, which is present inside at a constant vertical interval. In this case, the water distributor 8c is a horizontal pipe having a hole opened downward, and the upper part thereof is fixed by an inclined flat plate.

On the other hand, in FIG. 1, reference numeral 12 denotes a refrigerator 12 which is provided outside the duct and supplies brine of 0 ° C. or less to the horizontal heat transfer tube group 5, and between the refrigerator 12 and the horizontal heat transfer tube group 5. Has a circuit for returning brine to the refrigerator 12 again.

Next, the operation of the gas turbine intake air cooling device constructed as described above will be described. The branch intake duct 1a provided with the vertical cooling plate 4 is selected by the flow path switching damper 2 to introduce the intake air 3 at the peak of the electric power load in the daytime, and the branch intake duct 1b is connected to the flow path switching damper 2 at the off-peak time at night. It is assumed that the intake air 3 is introduced by selecting by.

First, the operation at night during off-peak hours will be described. In the branch intake duct 1a, in the ice heat storage container 6 installed above the air cooling panel 4, brine below 0 ° C. from the refrigerator 12 is horizontally transferred. Water is pumped from the bottoms of the water storage plate 7 and the ice heat storage container 6 by the water circulating water pump 28 through the pipe of the heat pipe (ice adhesion pipe) 5 group, and water is supplied from above the ice adhesion pipe 5 group to generate static ice. Accumulate and accumulate ice.

During ice making in the ice heat storage container 6, as shown in detail in FIG. 7, the water 13 falling (flowing down) from the water distributor 8 is horizontally transferred by passing a brine 15 at a temperature of 0 ° C. or less through a pipe. It is cooled by 5 groups of heat tubes and frozen to become static ice 14.

Next, the operation at the peak of daytime electric power load will be described. When the water vapor 17 evaporated from the vertical cooling plate 4 rises into the ice heat storage container 6, the horizontal transmission is performed as shown in FIG. 8 in detail. It condenses on the surface of the ice 14 that has adhered and accumulated to the group of heat tubes 5 and melts the ice 14 on the surface. Here, when the number of horizontal heat transfer tubes 5b in the vertical direction increases, the amount of condensed / melted water 13 that flows down increases, and the condensation performance deteriorates on the surface of the ice 14. Therefore, the water distributor 8c is placed every fixed number of vertical steps. The inclined flat plate which is installed and which fixes the water distributor 8c guides the water 13 to the inner wall 16 in the ice heat storage container 6. This can prevent the condensation performance on the surface of the ice 14 from decreasing.

At this time, the amount of water supplied into the vertical cooling plate is adjusted by the float type water level controller 11 from the water reservoir 9 partitioned by the weir 10 into the vertical cooling plate 4. By adjusting the flow amount, the amount of water vapor evaporated on the vertical cooling plate 4 can be made constant.

With the gas turbine intake air cooling device having such a configuration, the following effects can be obtained. During the summer daytime, a large amount of intake air is cooled during the peak power load of 2-3 hours. Therefore, the sensible heat of water (1 kcal / kg) and the heat of melting of ice (80 kcal / kg) alone are enough for the amount of ice (ice filling). Ratio: The weight ratio of ice to water is about 30% even if it is increased, and even if the amount of sensible heat of return water (return temperature is 12 ° C) can be used, a considerably large ice heat storage tank is required. . On the other hand, if the latent heat of vaporization of water (597 kcal / kg) can be used, it is possible to cool the intake air with a small amount of water. That is, 3
Comparing the amount of cold heat per unit mass with an ice heat storage tank having an ice filling rate of 0%, 597 / (0.3 × 80 + 12) = 1
Since this is 6.58, intake air cooling can be supported with a sufficiently small mass (water amount).

In this case, since the evaporation temperature of water is about 5 ° C. to cool the intake air temperature, it is necessary to evaporate the water in a high vacuum. However, in the full-fill type evaporator, water pressure is applied depending on the water depth. , It's impossible.

Therefore, in the present embodiment, not only the heat transfer tube group is constituted, but a system in which water is made to flow down into a vertical cooling panel to evaporate, and the inside of the ice heat storage container 6 is vacuumized by communicating with the vertical cooling plate 4. Since the state is set, it becomes possible to cool the intake air with a low heat transfer area and a low pressure loss by allowing water to flow down and evaporate.

As shown in FIG. 5, the vertical cooling plate 4 is constructed by sandwiching a gutter-shaped beam 23 which is inclined by 10 degrees or more with respect to the plane between two flat plates as shown in FIGS. Since the connection portion between the gutter-shaped beam 23 and the flat plate has a divergent shape, the water 22 flowing down in the vertical cooling plate 4 can flow down while alternately flowing in and out on the inner walls of the opposed flat plates 4a and 4b. Therefore, the falling liquid film formed on the inner wall of the vertical cooling plate 4 is disturbed, and the evaporation performance can be improved.

Further, since the porous chamber surface 25 is formed by copper spraying on the inner walls of the flat plates 4a, 4b through which the water 22 flows down, the evaporation heat transfer characteristic can be improved. Further, since the water content in the air is condensed on the outer wall of the vertical cooling plate 4 to cool the intake air 3, the horizontal groove 26 is formed as shown in FIG.
Since the vertical ribs 27 are fixed at regular intervals, condensed water is caused to flow along the horizontal groove 26, and the condensed water is blocked by the vertical ribs 27 so as to flow downward in the vertical direction. It can be prevented from being accompanied.

[0041]

As described above, according to the present invention, in order to cool the intake air in the intake passage of the gas turbine, the vertical cooling plate is installed in parallel with the intake flow, and water flows down in the cooling plate. In order to perform liquid film evaporation, it was arranged to condense the water vapor with high vacuum on the static ice in the upper ice heat storage container that is in communication with the cold plate accumulated at the time of low power load at night,
It is possible to provide a gas turbine intake air cooling device that can reduce the cooling area, reduce the pressure loss that occurs during intake air cooling, and increase the output of the gas turbine.

[Brief description of drawings]

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

FIG. 2 is a view of the gas turbine intake air cooling device of the embodiment as seen from the intake side.

FIG. 3 is a vertical cross-sectional view of a vertical cooling plate in the example.

FIG. 4 is a structural diagram of a gutter-shaped beam in a vertical cooling plate in the example.

FIG. 5 is a horizontal sectional view of a vertical cooling plate according to the embodiment.

FIG. 6 is an explanatory diagram of a connection state between a vertical cooling plate group and an upper ice heat storage container in the same embodiment.

FIG. 7 is a view showing an ice adhering state in the ice heat storage container in the embodiment.

FIG. 8 is a view showing a condition of melting ice in the ice heat storage container in the embodiment.

[Explanation of symbols]

1 ... Intake duct, 1a, 1b ... Branch intake duct, 2
...... Flow path switching damper, 3 ...... Air, 4 ...... Vertical cooling plate, 5, 5a, 5b ...... Ice adhering pipe group, 6 ...... Ice heat storage container, 7 ...... Water storage plate, 8a, 8b, 8c ... ... water distributor,
9 ... Water reservoir, 10 ... Weir, 11 ... Float type liquid level controller, 12 ... Refrigerator, 13 ... Ice, 14 ... Ice, 1
5 ... Prine, 16 ... Inner wall of ice heat storage container, 17 ... Steam, 18 ... Condensed water, 19 ... Top of intake duct, 2
0 ... upper part of vertical cooling plate, 21 ... notch for water supply,
22 ... Water flowing down into the air cooling pipe, 23 ... Oblique gutter-shaped beam, 24 ... Spreading part of gutter, 25 ... Porous surface,
26 ... Horizontal groove, 27 ... Vertical rib, 28 ... Circulating water pump.

Claims (6)

[Claims] 1. An intake duct forming a suction flow path for combustion air of a gas turbine is branched into two parts, and a flow path switching damper is provided at the branch part, and two branch intake air ducts are provided in one of the branch intake ducts. A plurality of cooling plates, each of which has a hollow portion formed by a flat plate, are vertically installed at appropriate intervals so as to be parallel to the flow direction of the intake air, and the upper portion of each cooling plate is placed in the hollow portion. A gas turbine intake air cooling device, characterized in that cold water is guided to be evaporated by the intake air of the gas turbine. 2. An intake duct that forms a suction flow path for combustion air of a gas turbine is branched into two, and a flow path switching damper is provided at the branch portion, and two flat plates are provided in one of the branch intake ducts. A plurality of cooling plates with a hollow inside are installed vertically with an appropriate interval so as to be parallel to the flow direction of the intake air, and at the same time, the water supply unit and the ice are installed on the upper surface of the branch intake duct. An ice heat storage container having a heat storage unit is provided so as to communicate with the hollow portion from the upper portion of each of the cooling plates, and water flowing down from the water supply unit of the ice storage container through the ice heat storage unit is hollow in each of the cooling plates. A gas turbine intake air cooling apparatus, characterized in that the gas turbine intake air is introduced into a gas turbine to be evaporated in a high vacuum state by the gas turbine intake air. 3. An ice heat storage section of an ice heat storage container, which is arranged at an upper portion and a side portion and has a group of horizontal heat transfer tubes to which static ice is adhered by brine of 0 ° C. or less which is passed from a refrigerator, The gas turbine intake system according to claim 2, further comprising: a water distributor, which is arranged on each of an upper portion, a lateral portion of the upper portion, and a lateral portion of the intermediate portion, and which supplies water to the outer surface of the horizontal heat transfer tube group from the upper portion. Cooling system. 4. A water distributor, which is arranged on the side of an intermediate portion of an ice heat storage container, has a horizontal pipe group having a hole at the bottom thereof, the horizontal pipe groups are arranged obliquely, and the upper portion thereof is fixed by a flat plate. The gas turbine intake air cooling device according to claim 3, wherein 5. The gas turbine intake according to claim 1, wherein the cooling plate is provided so that a gutter-shaped beam inclined by 10 degrees or more with respect to a horizontal plane is sandwiched between two flat plates. Cooling system. 6. The two flat plates constituting the cooling plate have a porous surface formed by copper spraying on an inner wall through which water flows down, and an outer wall which exchanges heat with air is provided with vertical ribs at regular intervals based on a horizontal groove. The gas turbine intake air cooling device according to claim 1 or 2, characterized in that.