JPH11315800A - Air compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To maintain strength of the components for stable operation by providing a stage of combined stationary and moving blades and, a cooling medium supplying means for supplying the cooling medium via the stationary blade on a cavity formed in the rotor disk. SOLUTION: A stationary blade 14 is fixed to a casing 13, inside which a hollow portion 21 is configured, one end of the hollow portion is supported by a circular inner ring 23 on which a labyrinth seal 22 is implanted, and this inner ring 23 is opposed to a cavity 24 which is formed in a rotor disk 17. The intake atmosphere is cooled by a heat exchanger 11, supplied to the hollow portion 21 for cooling. Then the air, after cooling the stationary blade 14, is supplied to the cavity 24 of the rotor disk 17 via a labyrinth seal 22 of the inner ring 23. The air, after cooling the rotor disk 17, passes the gap of the labyrinth 22 again to meet the air compressor driving air. The strength of components is thereby maintained for stable operation.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air compressor, and more particularly to an air compressor for effectively cooling components such as a stationary blade and a rotor disk (rotary shaft) housed in the air compressor.

[0002]

2. Description of the Related Art Conventionally, a gas turbine plant applied for power generation includes an air compressor 1, a gas turbine combustor 2, a gas turbine 3, and a generator 4, as shown in FIG. The acidified air is compressed into high-pressure air,
Fuel is added to the high-pressure air to generate combustion gas in the gas turbine combustor 2, and the combustion gas is supplied to the gas turbine 3 to perform expansion work to generate rotation torque. It is driven to generate electric power. In this case, the gas turbine plant generates a rotational torque in the gas turbine 3 with the energy of the fuel supplied to the gas turbine combustor 2, and the rotational torque is distributed to the drive of the generator 4. The energy of the fuel that generates the power is only about 35%, and most of the energy of the fuel is released to the atmosphere.

[0003] For example, a combined cycle power plant has recently attracted attention as a power plant that has improved the thermal efficiency of a plant by skillfully combining such gas turbine plants with low plant thermal efficiency.

As shown in FIG. 14, this combined cycle power plant is a combination of a gas turbine plant 5 with a steam turbine plant 6 and an exhaust heat recovery boiler 7, and the exhaust gas after expansion work discharged from the gas turbine 3. Is supplied to a waste heat recovery boiler 7 as a heat source. Here, steam is generated by water supplied from a steam turbine plant 6, and the steam is supplied to a steam turbine 8 to perform expansion work. The generator 9 is driven by the torque to generate electric power.

As described above, the gas turbine plant 5
In the combined cycle power plant in which the steam turbine plant 6 and the exhaust heat recovery boiler 7 are combined, since the energy of the exhaust gas discharged from the gas turbine 3 is skillfully utilized, the plant thermal efficiency can be improved to about 50%. it can.

In recent combined cycle, in order to further improve the thermal efficiency of the plant, the temperature of the combustion gas supplied from the gas turbine combustor 2 to the gas turbine 3 has been increased, and the air compressor 1 has been developed to have a higher pressure ratio. Has been done.

Conventionally, in a gas turbine plant in which the temperature of the combustion gas supplied from the gas turbine combustor 2 to the gas turbine 3 is 1100 ° C., the pressure ratio of the air compressor 1 is set to 10 to 10.
It is often selected in the range of 15.

However, recently, the temperature of the combustion gas supplied from the gas turbine combustor 2 to the gas turbine 3 is 1300 ° C.
In a gas turbine plant upgraded to a class, a gas turbine in which the pressure ratio of the air compressor 1 becomes 15 or more is adopted. In addition, 150
In a 0 ° C.-class gas turbine plant, development is being made to make the pressure ratio of the air compressor 1 20 to 30.

When the pressure ratio of the air compressor 1 becomes 20 to 30, the high-pressure air discharged from the air compressor 1
As shown in FIG. 5, since the temperature exceeds 400 ° C., the flow rate of fuel injected into the gas turbine combustor 2 is further reduced as compared with the conventional case, and further improvement in plant thermal efficiency is expected.

[0010]

When the pressure ratio of the air compressor 1 becomes 20 to 30, the gas turbine plant has several problems that must be solved. There is strength.

Conventionally, as a material applied to the stationary blades, the rotor disk, and the like of the air compressor 1, for example, 12 chromium alloy steel which is relatively inexpensive and has excellent workability has been used.

However, the pressure ratio of the air compressor 1 is 20 to 3
When it becomes 0, it is applied to stationary blades, rotor disks, etc. 1
As shown by the broken line in FIG. 16, the temperature of the high-pressure air in the 2-chromium alloy steel is too high, so that the creep strength may be rapidly reduced and long-term stable operation may be difficult.

In order to maintain a high creep strength of the stationary blades and the rotor disk, and to ensure a long-term stable operation of the air compressor 1, at present, no new material has been developed, and a cooling technique is required as an alternative. Is done.

The present invention has been made based on such background art, and provides an air compressor in which the creep strength of the components of the air compressor is maintained at a high level and a long-term stable operation of the air compressor is achieved. The purpose is to do.

Another object of the present invention is to provide an air compressor which effectively utilizes a cooling medium for cooling the components of the air compressor.

[0016]

In order to achieve the above object, an air compressor according to the present invention is characterized in that, as described in claim 1, a vane is provided along an axial direction of a rotor disk housed in a casing. A cooling medium supply means for supplying a cooling medium through the stationary blade is provided in a cavity formed in the rotor disk, the paragraph including a stage in which a moving blade is combined.

Further, in order to achieve the above object, the air compressor according to the present invention comprises a cooling medium supply means for exchanging heat with cooling air provided separately from the air compressor. It is composed of a container.

Further, in order to achieve the above object, the air compressor according to the present invention forms a hollow portion in the stationary blade and supports an end of the stationary blade. A cavity is formed in the rotor disk facing the inner ring, and the cooling medium from the hollow portion of the blade is supplied to the cavity, and then merged with the air driven by the air compressor.

Further, in order to achieve the above object, the air compressor according to the present invention forms a hollow portion in the stationary blade and blows the hollow portion into the hollow portion. An outlet is provided.

In order to achieve the above object, in the air compressor according to the present invention, the air outlet is formed at a position within 15% of the blade height of the stationary blade. It was done.

In order to achieve the above object, the air compressor according to the present invention is such that the outlet is formed along the back side of the stationary blade.

In order to achieve the above object, the air compressor according to the present invention is such that the outlet is formed at the end of the stationary blade facing the rotor disk. is there.

Further, in order to achieve the above object, the air compressor according to the present invention, as described in claim 8, has a blade hollow portion formed in a stationary blade, and this blade hollow portion is formed in the stationary blade. After extending to the inner ring supporting the wing, the cooling medium from the hollow portion of the wing is supplied to the inner ring, and then combined with the air driven by the air compressor.

Further, in order to achieve the above object, the air compressor according to the present invention forms a hollow portion in the stationary blade and supports an end of the stationary blade. An inner ring hollow portion is formed in the inner ring, and an outlet that communicates with the inner ring hollow portion and causes the cooling medium from the wing hollow portion to jet and collide with the rotor disk is formed in the inner ring.

Further, in order to achieve the above object, an air compressor according to the present invention has a vane hollow portion formed in a vane and supports an end of the vane. An inner ring hollow portion is formed in the inner ring to be formed, and an outlet that communicates with the inner ring hollow portion and blows out the cooling medium from the blade hollow portion along the root portion side of the moving blade is formed in the inner ring.

Further, in order to achieve the above object, the air compressor according to the present invention is characterized in that high-pressure air from the outlet side of the air compressor is supplied to the middle stage of the air compressor. And a heat exchanger interposed in the air circulation system and exchanging the high-pressure air with the medium to be heated.

In order to achieve the above object, the air compressor according to the present invention is characterized in that the medium to be heated is fuel.

In order to achieve the above object, an air compressor according to the present invention combines a stationary blade and a moving blade along the axial direction of a rotor disk housed in a casing. In addition to forming a hollow portion in the stationary blade of the downstream stage, and forming a solid stationary blade in the upstream stage, the rotor disk is formed in a ring shape and joined with tie rods. The cavity formed in the rotor disk facing the stator blade having the blade hollow portion and the cavity formed in the rotor disk opposite to the stator blade having the blade hollow portion are separated from each other by the tie rod. A cavity formed in the rotor disk on the opposite side of the solid stator blade from a downstream passage, a cavity formed in the rotor disk facing the solid stator blade, and the tie rod. Those having an upstream passage communicating with each other and.

[0029] In order to achieve the above object, the air compressor according to the present invention comprises, as described in claim 14, a vane having a wing hollow portion comprising an upstream stage and a downstream stage. It is installed with a plurality of paragraphs.

In order to achieve the above object, an air compressor according to the present invention is provided with a gas turbine plant, a steam turbine plant and an exhaust heat recovery boiler in the air compressor. Combined with the exhaust heat recovery boiler of the combined cycle power plant, the cooling steam supply system for supplying steam from the exhaust heat recovery boiler to the air compressor, and the components accommodated in the air compressor were cooled. A steam recovery system for recovering steam to the exhaust heat recovery boiler.

In order to achieve the above object, the air compressor according to the present invention is characterized in that high-pressure air from the outlet side of the air compressor is supplied to the middle stage of the air compressor. An air flow control valve for controlling the flow rate of the high-pressure air, a heat exchanger for cooling the high-pressure air, and cooling supplied to the heat exchanger. A cooling medium flow control valve for controlling the flow rate of the medium, and a control operation unit for providing a valve opening / closing signal to the air flow control valve and the cooling medium flow control valve are provided.

In order to achieve the above object, in the air compressor according to the present invention, as set forth in claim 17, the control operation unit includes a control unit for controlling the suction air pressure signal of the air compressor and the air compressor. A pressure ratio of the air compressor is calculated based on a pressure signal of the compressed high-pressure air, and a valve opening / closing signal is calculated based on the calculated pressure ratio and a temperature signal of the high-pressure air,
The arithmetic signal is supplied to the air flow control valve and the cooling medium flow control valve to control the flow rates of the high-pressure air and the cooling medium.

[0033]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of an air compressor according to the present invention will be described below with reference to the drawings and the reference numerals in the drawings.

FIG. 1 is a schematic sectional view showing a first embodiment of the air compressor according to the present invention.

The air compressor according to the present embodiment is a cooling air compressor 10 that compresses the sucked air into high-pressure air.
A heat exchanger 11 for once cooling the high-pressure air, and a cooling air system 15 for supplying the high-pressure air cooled by the heat exchanger 11 to the stationary blades 14 housed in the casing 13 of the air compressor 12.
It is configured to have:

The cooling air compressor 10 includes an air compressor 12
And a drive unit 16 such as a motor.

On the other hand, the air compressor 12 includes a casing 13
A rotor disk (rotating shaft) 17 in a ring shape is accommodated therein, and fixed to the rotor blade 17 and the casing 13 implanted in the rotor disk 17 in an annular passage 18 formed between the rotor disk 17 and the casing 13. The stage 20 is configured by combining with the stationary blades 14, and the stage 20 is arranged in multiple stages along the flow of the air compressor drive air AR.

The stationary blade 14 fixed to the casing 13
Is formed such that a hollow hollow portion 21 is formed therein, one end of which is supported by an annular inner ring 23 in which a labyrinth 22 is implanted, and the inner ring 23 faces a cavity 24 formed in the rotor disk 17. I have.

In forming the wing hollow portion 21, the stationary blade 14 may be formed by machining or by forming a ventral side in which the wing hollow portion 21 is formed in advance and a back side in which the wing hollow portion 21 is formed in advance. Is selected. When the profile of the stationary blade 14 uses a three-dimensional blade element design method, the blade hollow portion 21 may be formed by precision casting. Further, in the case where the solid stationary blades 14 and the stationary blades 14 of the blade hollow portion 21 are arranged in a mixed manner with respect to the plurality of paragraphs 20, in order to make the circumferential flow of the air compressor drive air AR uniform, It is desirable that the outer shape of the stationary blade 14 of the hollow portion 21 be the same as that of the solid stationary blade 14. Further, when a large amount of cooling air is required or when the number of the stationary blades 14 of the blade hollow portion 21 is reduced due to a problem of processing cost, the stationary blade 14 of the blade hollow portion 21 has a blade thickness ratio and a blade cord length. It is desirable to make it larger than that of the solid stationary blade 14.

Next, the operation of the air compressor according to this embodiment will be described.

The air compressor 12 is provided with an air compressor driving air A
When R is passed through the stage 20 in which the stationary blades 14 and the moving blades 19 are combined, the pressure is increased by compression, and the air for driving the air compressor AR is increased in temperature with the increase in pressure.

When the temperature of the air compressor driving air AR becomes high,
As shown in FIG. 14, the stationary blades 14 and the rotor disk 17 have a rapid decrease in creep strength, making it difficult to perform long-term operation.

In the present embodiment, in consideration of such a point, the cooling air compressor 10 is driven by the driving device 16 and
The sucked atmosphere is compressed to have a higher pressure than the air compressor drive air AR, and further, in the heat exchanger 11, for example, 250 ° C.
After cooling, the blade hollow portion 21 of the stationary blade 14 is used for cooling.
To supply.

The air that has cooled the stationary blades 14 is
The air is supplied to the cavity 24 of the rotor disk 17 through the labyrinth 22, where the rotor disk 17 is cooled, and then joins the air compressor driving air AR again through the gap of the labyrinth 22.

As described above, in the present embodiment, the cooling air compressor 10, the heat exchanger 11, and the cooling air system 15 are provided, and the high-pressure air compressed by the cooling air compressor 10 is
The cooling air was supplied to the blade hollow portion 21 of the stationary blade 14 and the cavity 24 of the rotor disk 17 through the cooling air system 15 for cooling, and the stationary blade 14 and the rotor disk 17 were cooled. Pressure ratio of machine 12
Even with the above, the strengths of the stationary blade 14 and the rotor disk 17 can be maintained high, and the air compressor 12 can perform long-term stable operation.

FIG. 2 is a schematic sectional view showing a second embodiment of the air compressor according to the present invention. The same components as those of the first embodiment are denoted by the same reference numerals.

In the present embodiment, an air outlet 25 is provided for allowing the cooling air CA to flow out of the blade from the blade hollow portion 21 of the stationary blade 14.

As shown in FIG. 3, the air outlet 25 is formed so as to extend from the blade hollow portion 21 of the stationary blade 14 to the back side 26 and to extend along the streamline of the back side 26. The position is formed within 15% of the blade height of the stationary blade 14.

As described above, in this embodiment, the air outlet 25 is provided from the blade hollow portion 21 of the stationary blade 14 toward the back side 26, and the cooling air CA from the blade hollow portion 21 of the stationary blade 14 is supplied to the air outside the blade. Since it merges with the compressor drive air AR, the rotor disk 1
Compressor driving air A, which caused the temperature rise of 7,
R can be kept low, and the rotor disk 17
Of the air compressor 12 can be maintained at a high pressure ratio.

In the present embodiment, the position of the air outlet 25 is set at a position within 15% of the blade height of the stationary blade 14,
Since the surface of the rotor disk 17 is covered with the cooling air CA flowing out of the outlet 25,
Can be shielded from the heat of the air compressor drive air AR.

In this embodiment, the outlet 25 is connected to the stationary blade 1.
4 is formed from the hollow part 21 of the blade to the back side 26, and the cooling air CA is blown out from the outlet 25 toward the corner part of the rotor disk 17 by a high-speed flow. This can improve the blade efficiency of the stationary blade 14.

FIG. 4 is a schematic sectional view showing a third embodiment of the air compressor according to the present invention. The same components as those of the first embodiment are denoted by the same reference numerals.

In this embodiment, an air outlet 25 is provided at the end of the stationary blade 14 facing the rotor disk 17 so as to communicate with the hollow blade portion 21.

As described above, in the present embodiment, at the end of the stationary blade 14, the outlet 25 communicating with the blade hollow portion 21 is provided,
Since the cooling air CA from the outlet 25 flows in the form of a film along the surface of the rotor disk 17, the rotor disk 17 can be shielded from the heat of the air compressor driving air AR,
The strength of the rotor disk 17 can be maintained high, and a high pressure ratio of the air compressor 12 can be realized.

FIG. 5 is a schematic sectional view showing a fourth embodiment of the air compressor according to the present invention. The same components as those of the first embodiment are denoted by the same reference numerals.

In the present embodiment, a labyrinth 22 is implanted in an inner ring 23 that supports an end of the stationary blade 14 facing the rotor disk 17, and the cooling air CA flowing out of the blade hollow portion 21 by the labyrinth 22 is transferred to the stationary blade. 14 are distributed so as to flow to the respective sides of the leading edge 27 and the trailing edge 28 of the stationary blade 14.

The present embodiment focuses on the point that the cooling air CA is higher than the pressure of the air compressor driving air AR, and the cooling air CA flowing out of the blade hollow portion 21 of the stationary blade 14 by the labyrinth 22 is Can be assigned to each of the leading edge 27 side and the trailing edge 28 side.

Therefore, according to the present embodiment, the stationary blade 1
Since the cooling air CA flowing out of the blade hollow portion 21 of No. 4 is distributed to the leading edge 27 side and the trailing edge 28 side of the stationary blade 14 by the labyrinth 22 and flows, the rotor disk 17 supporting the moving blade 19 is cooled. As a result, the strength of the rotor disk 17 can be maintained high, and a high pressure ratio of the air compressor 12 can be realized.

FIG. 6 is a schematic sectional view showing a fifth embodiment of the air compressor according to the present invention. The same components as those of the first embodiment are denoted by the same reference numerals.

In this embodiment, an inner ring hollow portion 29 is formed in an annular inner ring 23 that supports the end of the stationary blade 14, and the cooling air CA from the blade hollow portion 21 is communicated with the inner ring hollow portion 29. An outlet 30 for ejecting the rotor disk 17 and the cavity 24 is formed. In this embodiment, although not shown, the wing hollow portion 21 is not shown.
The stator vanes 14 provided with the solid vanes 14 and the solid vanes are mixed along the circumferential direction to form a cascade, or, for example, a solid vane of the preceding paragraph is arranged, and Vane 1 equipped with
4 are arranged.

As described above, in the present embodiment, the wing hollow portion 2
1 or a solid stator vane along the circumferential direction, or, for example, a solid stator vane arranged in the preceding paragraph and a vane hollow part 21 provided in the rear paragraph. 14 is formed, and the stationary blade 1 having the blade hollow portion 21 is formed.
The cooling air CA from the airfoil hollow portion 21 is blown out almost uniformly toward the rotating rotor disk 17, and a portion where the cooling air CA hits the rotor disk 17 and a portion where the cooling air CA does not hit the rotor disk 17. Are alternately generated to prevent a periodic temperature change, so that the rotor disk 17 can be cooled well, the strength of the rotor disk 17 can be maintained high, and the air compressor 1
A high pressure ratio of 2 can be realized.

In the present embodiment, the cooling air CA is jet-collimated from the outlet 30 of the inner ring hollow portion 29 toward the rotating rotor disk 17. Can be cooled even more effectively.

FIG. 7 is a schematic sectional view showing a sixth embodiment of the air compressor according to the present invention. The same components as those of the first embodiment are denoted by the same reference numerals.

In the present embodiment, similarly to the fifth embodiment, an inner ring hollow portion 29 is formed in an annular inner ring 23 that supports the end portion of the stationary blade 14 and communicates with the inner ring hollow portion 29 to form a blade hollow. The cooling air CA from the part 21 is formed toward the root part (root) of the rotor blade 19 and has an outlet 31 formed therein. In this embodiment, the blade row is formed by mixing the stationary blades 14 having the blade hollow portions 21 and the solid stationary blades along the circumferential direction, or for example, the solid stationary blades in the preceding paragraph are formed. The blades are arranged, and the stationary blade 14 having the blade hollow portion 21 is arranged in a later stage to form a cascade.

As described above, according to the present embodiment, the inner ring hollow portion 29 and the outlet 31
Is formed, and the blade hollow portion 21 of the vane 14 is
Since the cooling air CA from the air flows into the root portion of the rotor blade 19 in a film form, the rotor disk 17 can be shielded from the heat of the air compressor driving air AR, and the strength of the rotor disk 17 can be maintained high. As a result, a high pressure ratio of the air compressor can be realized.

FIG. 8 is a schematic system diagram showing a seventh embodiment of the air compressor according to the present invention applied to a simple cycle (open cycle) gas turbine plant as an example.

A simple cycle (open cycle) gas turbine plant includes an air compressor 32, a gas turbine combustor 33, a gas turbine 34, and a generator 35.
The air sucked by the air compressor 32 is compressed to a high pressure,
The high-pressure air is supplied to the gas turbine combustor 33 together with the fuel, where combustion gas is generated. The combustion gas is supplied to the gas turbine 34 to perform expansion work, and power is generated by the rotational torque generated during the expansion work. The device 35 is driven.

In the present embodiment, the heat exchanger 36 is connected to an air circulation system 37 for bypassing part of the high-pressure air supplied from the air compressor 32 to the gas turbine combustor 33 and returning it to the intermediate stage of the air compressor 32 again. Is installed.

As described above, in the present embodiment, the air compressor 3
2 is provided with an air circulation system 37 interposed with a heat exchanger 36, bypasses a part of high-pressure air supplied from the air compressor 32 to the gas turbine combustor 33, and exchanges heat with fuel in the heat exchanger 36. And the high-pressure air is returned to the air compressor 32 again for cooling, and the components such as the stationary blades accommodated in the air compressor 32 are cooled, so that the air compressor is not wastefully consumed without energy. The components of the air compressor 32 can be cooled, the strength of the components can be maintained high, and a high pressure ratio of the air compressor 32 can be realized.

In this embodiment, the high-pressure air from the air compressor exchanges heat with the fuel in the heat exchanger 36 to heat the fuel and increase its internal energy. The expansion work can be performed by the heat treatment device 34, and the thermal efficiency of the plant can be improved.

FIG. 9 is a schematic sectional view showing an eighth embodiment of the air compressor according to the present invention. The same components as those of the first embodiment are denoted by the same reference numerals.

In this embodiment, the rotor disk 1 is provided in the casing 13 of the air compressor 12 and has a section 20 having a stage 20 formed by combining a stationary blade 14 and a moving blade 19.
7 are connected by a tie rod 38, and the downstream cavity 3 of the rotor disk 17 facing the stationary blade 14 having the blade hollow portion 21 located downstream from the tie rod 38.
9b, and a downstream passage 40b for communicating the downstream cavity 39b of the rotor disk 17 facing the opposite side of the stationary blade 14 with the blade hollow portion 21 with each other;
Upstream of the rotor disk 17 facing the solid stationary vane 41
And an upstream passage 40a for communicating the upstream cavity 39a of the rotor disk 17 and the upstream cavity 39a of the rotor disk 17 facing the opposite side of the solid stationary blade 41 with each other. The cooling air CA supplied to the first and second passages 21 and 40 is supplied to the downstream passage 40b and the upstream passage 40a by using pumping due to surface friction of the rotor disk 17.
The rotor disk 17 supporting the moving blade 41 in the preceding paragraph is cooled through the above.

Therefore, according to the present embodiment, the side passages 40a and the downstream passages 40b are formed on the upstream side and the downstream side of the rotor disk 17, respectively, and the pumping is performed from the downstream side passage 40b toward the upstream side passage 40a. Since the cooling air CA is caused to flow by the action to cool the rotor disks 17 in the preceding and following paragraphs, the strength of the rotor disks 17 can be maintained high, and a high pressure ratio of the air compressor 12 can be realized.

In this embodiment, the rotor disks 17 in the preceding and following paragraphs are cooled by the cooling air CA.
For example, as shown in FIG. 10, even when cooling air CA is flown from the vane 14 having the vane hollow portion 21 of interest to the vane 14 having the vane hollow portion 21 several paragraphs upstream from the vane 14 having the vane hollow portion 21. good. In this case, the passage 4 is provided in each of the rotor disks 17 and 17.
2, 42 are formed.

FIG. 11 is a schematic system diagram showing a ninth embodiment of the air compressor according to the present invention applied to a combined cycle power plant as an example.

A combined cycle power plant is a gas turbine plant 43 composed of an air compressor 32, a gas turbine combustor 33, a gas turbine 34, and a generator 35, and a steam turbine plant composed of a steam turbine 44 and a generator 45. 46 and waste heat recovery boiler 47
A steam is generated by an exhaust heat recovery boiler 47 using exhaust gas discharged from the gas turbine 34 as a heat source, and the steam is supplied to a steam turbine plant 46 to perform expansion work, which is generated during expansion work. The generator 45 is driven by the rotating torque that changes.

In this embodiment, when the pressure ratio of the air compressor 32 is set to 30, the temperature of the high-pressure air becomes approximately 550 ° C.
Steam suitable for cooling this temperature is supplied to the exhaust heat recovery boiler 47.
And a cooling steam supply system 48 for supplying steam for cooling from the exhaust heat recovery boiler 47 to components such as the stationary blades of the air compressor 32, and cooling the components. The exhausted steam is discharged into the waste heat recovery boiler 47.
And a steam recovery meter 49 for recovery.

As described above, in this embodiment, the steam generated from the exhaust heat recovery boiler 47 is used for cooling the air compressor 3.
2 and a steam recovery system 49 for recovering the steam after cooling the components to the exhaust heat recovery boiler 47, and utilizing the large specific heat of the steam to air Since the components of the compressor are cooled, the components of the air compressor can be cooled even better, their strength can be maintained high, and a high pressure ratio of the air compressor 32 can be realized. Can be.

FIG. 12 is a schematic control system diagram showing a tenth embodiment of the air compressor according to the present invention applied to a simple cycle (open cycle) gas turbine plant as an example. The same parts as those of the seventh embodiment are denoted by the same reference numerals.

In this embodiment, the flow of the high-pressure air is supplied to the air circulation system 37 which bypasses part of the high-pressure air supplied from the air compressor 32 to the gas turbine combustor 33 and returns to the intermediate stage of the air compressor 32 again. The air flow control valve 50 and the heat exchanger 36 are provided in this order, and the heat exchanger 36 is provided with a cooling medium flow control valve 52 in a cooling medium supply system 51 that supplies a cooling medium, for example, water. The pressure ratio of the air compressor 32 is calculated based on the atmospheric pressure signal detected by the pressure gauge and the high pressure air pressure signal detected by the pressure gauge 54, and based on the calculated pressure ratio and the actual high pressure air temperature signal from the thermometer 55. A control operation for calculating the valve opening / closing signal and applying the calculated signal to the air flow control valve 50 and the cooling medium flow control valve 52 to control the air flow control valve 50 and the cooling medium flow control valve 52 to open and close. Parts 56 in which the provided.

As described above, in the present embodiment, the air flow regulating valve 50 and the heat exchanger 36 interposed in the air circulation system 37 are provided.
A control operation unit 56 for controlling the opening and closing of each of the cooling medium flow adjustment valves 52 interposed in the air conditioner is provided, and the operation flow of the air flow adjustment valve 50 and the cooling medium flow adjustment valve 52 is controlled by an operation signal from the control operation unit 56, and Since a part of the high-pressure air from the compressor 32 is cooled to an appropriate temperature to cool the components such as the stationary blades accommodated in the air compressor 32, the components of the air compressor 32 can be used without wasting energy. Can be reliably cooled, the strength of the component parts can be maintained high, and a high pressure ratio of the air compressor 32 can be realized.

[0082]

As described above, the air compressor according to the present invention is provided with the cooling supply means for satisfactorily cooling the components housed in the air compressor, thereby maintaining the strength of the components high. Thus, the air compressor can perform a long-term stable operation to realize a high pressure ratio.

Further, the air compressor according to the present invention is provided with a means for effectively utilizing the cooling medium for cooling its components without wasting it, so that the thermal efficiency of the plant can be further improved.

At this time, since the control means for controlling the temperature of the cooling medium to an appropriate temperature is provided, the components of the air compressor can be cooled even better.

[Brief description of the drawings]

FIG. 1 is a schematic sectional view showing a first embodiment of an air compressor according to the present invention.

FIG. 2 is a schematic sectional view showing a second embodiment of the air compressor according to the present invention.

FIG. 3 is a sectional view taken along the line AA of FIG. 2;

FIG. 4 is a schematic sectional view showing a third embodiment of the air compressor according to the present invention.

FIG. 5 is a schematic sectional view showing a fourth embodiment of the air compressor according to the present invention.

FIG. 6 is a schematic sectional view showing a fifth embodiment of the air compressor according to the present invention.

FIG. 7 is a schematic sectional view showing a sixth embodiment of the air compressor according to the present invention.

FIG. 8 is a schematic system diagram showing a seventh embodiment of an air compressor according to the present invention applied to a simple cycle (open cycle) gas turbine plant as an example.

FIG. 9 is a schematic sectional view showing an eighth embodiment of the air compressor according to the present invention.

FIG. 10 is a schematic sectional view showing an eighth embodiment of the air compressor according to the present invention.

FIG. 11 is a schematic system diagram showing a ninth embodiment of an air compressor according to the present invention applied to a combined cycle power plant as an example.

FIG. 12 is a schematic system diagram showing a tenth embodiment of an air compressor according to the present invention applied to a simple cycle (open cycle) gas turbine plant as an example.

FIG. 13 is a schematic system diagram showing a conventional simple cycle (open cycle) gas turbine plant.

FIG. 14 is a schematic system diagram showing a conventional combined cycle power plant.

FIG. 15 is a diagram showing the relationship between the temperature of high-pressure air and the pressure ratio of the air compressor.

FIG. 16 is a diagram showing a relationship between strength and temperature of a material applied to a component of the air compressor.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Air compressor 2 Gas turbine combustor 3 Gas turbine 4 Generator 5 Gas turbine plant 6 Steam turbine plant 7 Exhaust heat recovery boiler 8 Steam turbine 9 Generator 10 Cooling air compressor 11 Heat exchanger 12 Air compressor 14 Casing 14 Stator Blade 15 Cooling Air System 16 Drive 17 Rotor Disk 18 Passage 19 Moving Blade 20 Paragraph 21 Blade Hollow Part 22 Labyrinth 23 Inner Ring 24 Cavity 25 Outlet 26 Back Side 27 Front Edge 28 Rear Edge 29 Inner Ring Hollow Section 30, 31 Blowing Outlet 32 Air compressor 33 Gas turbine combustor 34 Gas turbine 35 Generator 36 Heat exchanger 37 Air circulation system 38 Tie rod 39a Upstream cavity 39b Downstream cavity 40a Upstream passage 40b Downstream passage 41 Moving blade 42 Passage 43 Gas turbine Plant 44 steaming Turbine 45 generator 46 steam turbine plant 47 exhaust heat recovery boiler 48 cooling steam supply system 49 vapor recovery system 50 the air flow rate control valve 51 coolant supply system 52 cooling medium flow control valves 53 and 54 a pressure gauge 55 thermometer 56 control arithmetic unit

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁶ Identification code FI // F02C 7/18 F02C 7/18 DA

Claims (17)

[Claims] 1. A cooling system comprising: a stage in which a stationary blade and a moving blade are combined along an axial direction of a rotor disk housed in a casing, wherein a cooling medium is supplied to a cavity formed in the rotor disk via the stationary blade. An air compressor provided with a medium supply means. 2. The air compressor according to claim 1, wherein the cooling medium supply means comprises a cooling air and a heat exchanger separately provided from the air compressor. 3. A wing hollow portion is formed in a stationary blade,
A cavity is formed in the rotor disk facing the inner race supporting the end of the stationary blade, and a cooling medium from the hollow portion of the blade is supplied to the cavity, and then combined with air driven by the air compressor. Item 7. The air compressor according to Item 1. 4. A wing hollow portion is formed in a stationary blade,
3. The air compressor according to claim 2, wherein an air outlet is provided in the hollow portion of the blade. 5. The air compressor according to claim 4, wherein the outlet is formed at a position within 15% of the blade height of the stationary blade. 6. The air compressor according to claim 4, wherein the outlet is formed along the back side of the stationary blade. 7. The air compressor according to claim 4, wherein the outlet is formed at an end of the stationary blade facing the rotor disk. 8. A wing hollow portion is formed in a stationary blade,
2. The air according to claim 1, wherein the airfoil hollow portion extends to an inner ring supporting the stationary blade, and after the cooling medium from the airfoil hollow portion is supplied to the inner wheel, the air is joined to the air compressor drive air. Compressor. 9. A hollow blade portion is formed in the stationary blade, and an inner ring hollow portion is formed in the inner ring supporting the end portion of the stationary blade. 2. An air compressor according to claim 1, wherein a blow-out port for jet-collimating the rotor with the rotor disk is formed in the inner ring. 10. A wing hollow portion is formed in a stationary blade,
Forming an inner ring hollow portion in the inner ring supporting the end of the stationary blade,
2. The air compressor according to claim 1, wherein an air outlet communicating with the hollow portion of the inner ring and blowing out the cooling medium from the hollow portion of the blade along the root portion side of the rotor blade is formed in the inner ring. 11. An air circulation system for returning high-pressure air from the outlet side of the air compressor to an intermediate stage of the air compressor, and an air circulation system interposed between the air circulation system and the high-pressure air for heating the medium to be heated. An air compressor comprising a heat exchanger to be exchanged. 12. The air compressor according to claim 11, wherein the medium to be heated is a fuel. 13. A stage in which a stationary blade and a moving blade are combined along the axial direction of a rotor disk housed in a casing, and among the paragraphs, a vane hollow portion is formed in a stationary blade of a downstream stage, and an upstream side is formed. While the stationary vane of the paragraph is formed solid, the rotor disk is formed in a sliced shape and connected by a tie rod, and the cavity formed in the rotor disk facing the stationary blade having the blade hollow portion with the tie rod as a boundary A downstream passage for communicating the stator blade provided with the blade hollow portion and the cavity formed on the rotor disk on the opposite side to each other, and a boundary between the cavity formed on the rotor disk facing the solid stator blade and the tie rod. An air compressor comprising: an upstream passage for communicating a cavity formed in the rotor disk on the opposite side of the solid stationary blade with each other. 14. The air compressor according to claim 13, wherein the stationary blade having the blade hollow portion is provided with a plurality of paragraphs between an upstream paragraph and a downstream paragraph. 15. A combined cycle power plant having an air compressor, a gas turbine plant, a steam turbine plant, and a waste heat recovery boiler, and combining steam from the waste heat recovery boiler with the air. An air compressor comprising: a cooling steam supply system for supplying to a compressor; and a steam recovery system for recovering, in the exhaust heat recovery boiler, steam having cooled components contained in the air compressor. . 16. An air circulation system for returning high-pressure air from the outlet side of the air compressor to an intermediate stage of the air compressor, and air interposed in the air circulation system for controlling a flow rate of the high-pressure air. A flow control valve, a heat exchanger for cooling the high-pressure air, a cooling medium flow control valve for controlling a flow rate of a cooling medium supplied to the heat exchanger, and a valve for the air flow control valve and the cooling medium flow control valve. An air compressor, comprising: a control operation unit that supplies an open / close signal. 17. The control arithmetic unit calculates a pressure ratio of the air compressor based on a suction atmospheric pressure signal of the air compressor and a pressure signal of high-pressure air compressed by the air compressor, and calculates the calculated pressure ratio. A valve opening / closing signal is calculated based on the ratio and the temperature signal of the high-pressure air, and the calculated signal is supplied to the air flow control valve and the cooling medium flow control valve to control the flow rates of the high-pressure air and the cooling medium, respectively. Claim 1.
6. The air compressor according to 6.