JP2010001821A - Variable stationary blade drive method and device for axial flow compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To extend the lifetime of an apparatus by preventing strong impact force from acting on a drive mechanism and a support part of an actuator ring, and improve operation reliability of stationary blades by eliminating angular errors between the plurality of stationary blades. <P>SOLUTION: In a variable stationary blade drive method for an axial flow compressor in which a ring 11 rotationally supported along a plurality of the variable blades 012 arranged annularly to surround a fluid channel "i", and the variable stationary blades 012 are rotated via a drive force transmission mechanism 05, the ring 11 is supported by being mounted on two guide rollers 13a, 13b disposed below the ring with an interval which is smaller than a diameter of the ring 11 and which enables stable support of the ring under a condition where the ring 11 is erected in a vertical direction, and directions of the variable stationary blades 012 are changed by rotating the ring 11 in a circumference direction under a condition where elastic force is applied on the ring 11 in a direction pressing the ring 11 on the guide rollers 13a, 13b. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an axial flow compressor such as a gas turbine, a turbo refrigerator, a jet engine or the like, and relates to a stationary blade driving method and apparatus for an axial flow compressor provided with a variable stationary blade mechanism. In addition to improving the life of the driving device, it is possible to eliminate angular errors between a plurality of variable vanes.

  In axial flow compressors such as jet engines, the stator blades are used to maintain and improve performance by controlling the amount of air intake during idling and high rotation, compared to the direction of the stator blades at the rated rotational speed. It is necessary to largely swing the direction of. This swing angle reaches, for example, 60 to 70 ° at the maximum. Therefore, in the axial flow compressor, a variable stationary blade mechanism is used in order to ensure operation stability in a wide operation range from low speed operation to high speed operation.

  FIG. 2 of Patent Document 1 (Japanese Patent Laid-Open No. 2000-345997) discloses an example of a variable stationary blade mechanism. This variable stationary blade mechanism will be described with reference to FIG. In FIG. 5, a ring-shaped actuator ring 01 is disposed so as to surround the fluid flow path f, and a large number of variable stationary blades 02 are annularly disposed along the actuator ring 01. A pinion 03 is attached to the shaft end of the stator blade shaft 02a integral with the variable stator blade 02, and a rack 04 that engages with the pinion 03 is formed on the entire surface of the actuator ring 01 facing the pinion 03. ing. The pinion 03 and the rack 04 constitute a variable stator vane driving force transmission mechanism 05.

  The actuator ring 01 is rotated (spinned) in the forward or reverse direction (arrow a or b direction) in the circumferential direction by an actuator (not shown), and the movement of the actuator ring 01 is transmitted to the variable stationary blade 02 via the driving force transmission mechanism 05. By doing so, the direction of the multiple stationary blades 02 with respect to the fluid flow f can be simultaneously changed to the same direction. In the gas turbine, the actuator ring 01 has a large diameter of 2 to 3 m and a large weight.

  FIG. 6 shows a drive mechanism of a variable inlet guide vane provided at the inlet of the compressor of the gas turbine. The inlet guide vane is one of the variable vanes provided around the air intake. In FIG. 6, the actuator ring 011 is vertically arranged at the inlet of the compressor of the gas turbine. A plurality of stationary blades 012 are arranged radially so as to surround the air intake port i along the actuator ring 011. The actuator ring 011 is supported by a plurality of guide rollers 013 arranged on the outer peripheral surface of the actuator ring 011 so as to be rotatable in the forward and reverse directions.

  The output shaft 010a of the actuator 010 is connected to a connection portion 014 provided on the outer peripheral surface of the actuator ring 011. The actuator ring 011 is rotated in the forward or reverse direction in the circumferential direction by the actuator 010. A stationary blade shaft 012a integrated with the variable stationary blade 012 is connected to the actuator ring 011 by a link mechanism, and is configured to rotate in conjunction with it. Therefore, the direction of the plurality of variable stationary blades 012 with respect to the air flow can be simultaneously changed to the same direction by rotating the actuator ring 011 in the circumferential direction. Thereby, the flow rate of the air flowing through the air intake i can be made variable.

  Japanese Patent Laid-Open No. 2006-138250 discloses various drive mechanisms for rotating an actuator ring in the circumferential direction. FIG. 4 of Patent Document 2 discloses a drive mechanism using a motor and a screw mechanism, and FIG. 5 discloses a pinion rack mechanism as described above. FIG. 6 discloses a drive mechanism using an electromagnet, and FIG. 7 discloses a drive mechanism using a hydraulic actuator. FIG. 8 discloses a drive mechanism using a differential pressure actuator.

  The drive mechanism disclosed in FIGS. 6 to 8 of Patent Document 2 has a protruding portion fixed in the radial direction of the actuator ring, and the pressure of the high pressure portion moves the piston in one direction by switching the electromagnet, the hydraulic actuator, or the valve. The protrusion is moved in the circumferential direction by a differential pressure actuator.

JP 2000-345997 A JP 2006-138250 A

  As described above, the actuator ring is supported by a plurality of guide rollers arranged around the actuator ring. FIG. 7 shows an example in which the actuator ring is supported by nine guide rollers. In FIG. 7, since the actuator ring 011 is erected in the vertical direction, it is substantially supported by two guide rollers 013e and 013f arranged below. Since the actuator ring 011 is large and heavy, a gap c is generated between the guide rollers other than the guide rollers 013e and 013f due to a dimensional error at the time of manufacture, an own weight of the actuator ring, or the like.

When the actuator 010 is driven in this state and the output shaft 010a of the actuator 010 is moved in the direction of the arrow a, the actuator ring 011 undergoes a slight revolving motion together with the circumferential rotation (spinning). Therefore, the actuator ring 011 gets over the guide roller 013e and collides with the guide roller 013d.
Similarly, when the actuator ring 011 rotates in the direction of arrow b, the actuator ring 011 gets over the guide roller 013f and collides with the guide roller 013g.

  When the actuator ring 011 collides with the guide roller 013d or 013g, an impact force is applied, so that the surface of the guide roller is cracked or the guide roller bearing is bent. In addition, a shocking force is applied to the drive unit such as the actuator 010 from the actuator ring 11 to shorten the life of the actuator 010 and the connection unit 014.

  Further, the revolving motion is a revolving motion around the guide roller 013a disposed in the upper part. Since such revolving motion occurs, the actuator ring 011 moves discontinuously, and the output of the actuator 010 is not accurately detected as the circumferential motion of the actuator ring 011 on the guide roller 013a or the variable stationary blade near the guide roller 013a. Phenomenon that is not transmitted to. Therefore, there arises a problem that an angle error occurs between a plurality of variable stationary blades.

  In view of the problems of the prior art, the present invention extends the life of these devices by preventing a large impact force from acting on the support portion and the drive mechanism of the actuator ring in the variable stator blade drive device of the axial flow compressor. An object of the present invention is to eliminate the angular error between a plurality of variable vanes and improve the operational reliability of the vanes.

In order to achieve the above object, a variable stator blade driving method for an axial compressor according to the present invention includes:
An axial flow compressor that rotates a ring supported rotatably along a plurality of variable stator blades arranged in an annular shape surrounding a fluid flow path, and rotates the variable stator blades via a driving force transmission mechanism. In the stationary blade driving method,
With the ring standing up and down, it is placed on and supported by two guide rollers that are smaller than the diameter of the ring and have an interval that enables stable support of the ring and is arranged below the ring,
An elastic force is applied to the ring in a direction in which the ring is pressed against the guide roller,
In this state, the ring is rotated in the circumferential direction to change the direction of the stationary blade.

  In the method of the present invention, when the ring is supported by a plurality of guide rollers, in addition to the two guide rollers that actually support the ring from below, a guide roller that does not participate in the support of the ring due to a gap formed with the ring Is not necessarily required. Instead, an elastic force is applied in the direction in which the ring is pressed against the two guide rollers, so that play between the ring and the guide roller is eliminated, and the ring can be stably supported by the guide roller.

As a result, when the ring is rotated (rotated) in the circumferential direction, the ring is always rotated without being separated from the two guide rollers, so that only the rotation motion is performed without causing the revolving motion. Accordingly, no angular error occurs between a plurality of stationary blades, and no collision with the guide roller occurs, so that no impact force acts on the ring support and the ring drive mechanism. Therefore, the life of the support part and the drive mechanism can be extended. Furthermore, the number of guide rollers can be reduced, and the number of parts of the ring support mechanism can be reduced, so that the cost can be reduced.
In the method of the present invention, in order to support the ring more reliably, installation of guide rollers other than the two guide rollers is not hindered.

Next, the variable stator blade drive device of the axial compressor of the present invention for carrying out the method of the present invention comprises:
A ring that is rotatably supported along a plurality of variable stator vanes that are annularly arranged around the fluid flow path, an actuator that rotates the ring in the forward or reverse direction in the circumferential direction, and a movement of the ring. In a variable stator blade drive device of an axial compressor having a driving force transmission mechanism that transmits to a variable stator blade,
Two guide rollers that support the ring in an upright direction, and that are smaller than the diameter of the ring and arranged below the ring with a spacing that enables stable support of the ring;
An elastic force application mechanism that applies an elastic force in a direction of pressing the ring against the guide roller,
The ring is rotated in the circumferential direction by the actuator while the ring is pressed against the guide roller by the elastic force applying mechanism.

  According to the apparatus of the present invention, the elastic force application mechanism rotates the ring in the circumferential direction while the ring is always pressed against the two guide rollers, so that no extra revolving motion other than the rotation motion occurs. Therefore, since the impact force does not act on the guide roller or the actuator drive unit, the guide roller or actuator drive unit is not damaged or cracked, and the life of these devices can be extended. In addition, no angular error occurs between a plurality of variable vanes. Furthermore, the number of guide rollers can be reduced, and the number of parts of the ring support mechanism can be reduced, so that the cost can be reduced.

In the apparatus of the present invention, the elastic force application mechanism is supported on the inner side of the ring via a spring member, and is pressed against the inner peripheral surface of the ring by the elastic force of the spring member, thereby pushing the ring against the guide roller. It is good to comprise with the 2nd guide roller which adds elastic force to the direction which hits.
As a result, the elastic force application mechanism can have a simple configuration. In addition, since the second guide roller is disposed inside the ring, the ring support portion does not increase in diameter, and the configuration of the compressor can be simplified.

  Further, in the device of the present invention, the elastic force applying mechanism is rotated by meshing with the rotational force applying belt disposed between the ring and the rotational force adding belt, the rotational force applying belt having both ends connected to the lower part of the ring. Thus, a belt wheel that rotates the ring in the circumferential direction, and a spring mechanism that applies an elastic force in a direction in which the rotational force adding belt is tensioned downward with respect to the belt wheel may be configured.

  In such a configuration, the guide roller is not disposed in the fluid flow path inside the ring, so that there is an advantage that the fluid flow is not obstructed. Further, since the ring rotates while applying a downward elastic force to the belt wheel, a force pressing the ring against the two guide rollers always acts, and no force in a direction in which the ring rides on the guide roller is generated. Therefore, there is no possibility that the ring gets over the guide roller.

  In the device of the present invention, an angle formed by two center lines connecting the center of the ring and the centers of the two guide rollers may be 60 to 100 °. When the angle exceeds 100 °, the surface pressure applied to the guide roller from the ring becomes excessive, and a large driving force is required to rotate the ring in the circumferential direction, and the guide roller is damaged by the excessive surface pressure. Or there is a risk of cracking. Conversely, if the angle is less than 60 °, the ring may get over the guide roller when the ring is driven.

  Therefore, by setting the angle to 60 to 100 °, the surface pressure of the ring applied to the guide roller can be reduced, the ring can be easily rotated, and the guide roller is not damaged or cracked. Life is possible and the ring can be stably supported by the guide roller.

In the device of the present invention, the guide roller is composed of two rollers rotatably connected by a connecting rod, and an intermediate portion of the connecting rod is pivotally attached to a support portion, It is good to comprise so that the load of a ring can be equally borne by two rollers.
As a result, the surface pressure per roller can be reduced by sharing the surface pressure of the ring applied to the guide roller by the two rollers. Further, since the load of the ring acting on the two rollers can be equally applied, the design can be performed with the minimum necessary safety factor.

  According to the method of the present invention, the ring that is rotatably supported along the plurality of annularly arranged variable stationary blades surrounding the fluid flow path is rotated, and the variable stationary blade is rotated via the driving force transmission mechanism. In a variable stator vane driving method of an axial flow compressor to be moved, the ring is placed on two guide rollers having a distance smaller than a diameter of the ring and capable of stably supporting the ring in a state where the ring is set up and down. In addition, the elastic force is applied to the ring in the direction of pressing the ring against the guide roller, and the ring is rotated in the circumferential direction in this state to change the direction of the stationary blade. As a result, a large impact force is not applied to the ring support and the drive mechanism, the service life of these rings can be extended, the angle error between the plurality of variable stator vanes can be eliminated, and the configuration can be simplified and the cost can be reduced. can do.

  Further, according to the device of the present invention, a ring that is rotatably supported along a plurality of annularly arranged variable vanes surrounding the fluid flow path, and rotates the ring in the forward or reverse direction in the circumferential direction. And a driving force transmission mechanism for transmitting the movement of the ring to the variable stator blade, wherein the ring is supported in an upright direction, and the ring is supported. Two guide rollers that are smaller than the diameter of the ring and arranged at a distance that enables stable support of the ring, and an elastic force application mechanism that applies an elastic force in a direction in which the ring is pressed against the guide roller. With the configuration in which the ring is rotated in the circumferential direction by the actuator in a state where the ring is pressed against the guide roller by the elastic force applying mechanism, it is possible to obtain the same operation effect as the method of the present invention. Kill.

  Hereinafter, the present invention will be described in detail with reference to embodiments shown in the drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the component parts described in this embodiment are not intended to limit the present invention to that only, unless otherwise specified.

(Embodiment 1)
A first embodiment in which the present invention is applied to a variable inlet guide vane (variable stationary vane) of a gas turbine will be described with reference to FIGS. 1 and 2. FIG. 1 schematically shows a stationary blade driving mechanism according to the present embodiment. In FIG. 1, the actuator ring 11 is arranged around the air intake port i together with a plurality of variable stator blades (not shown). It is supported by two guide rollers 13 a and 13 b arranged below the actuator ring 11. In FIG. 1, the variable stator blade is not shown.

  The actuator 10 is a hydraulic or electric actuator, and its output shaft 10 a is connected to a connection portion 14 fixed to the outer peripheral surface of the actuator ring 11. Then, by actuating the actuator 10, the actuator ring 11 can be rotated in the normal or non-return direction (arrow a direction or arrow b direction).

  A second guide roller 15 is disposed inside the actuator ring 11. The second guide roller 15 is supported by the fixed portion 17 via the spring member 16. That is, one end of the spring member 16 is connected to the fixing portion 17, and the other end of the spring member 16 is connected to the second guide roller 15. Thus, the second guide roller 15 is pressed against the inner peripheral surface of the actuator ring 11 by the elastic force of the spring member 16, and the actuator ring 11 is supported by the guide rollers 13a and 13b and the second guide roller 15 from both sides.

The center point of the actuator ring 11 _{O 1} and the guide roller 13a and the center line _{L 1} connecting the center point _{O 2} of the center line _{L 2} connecting the center point _{O 1} and the guide roller 13b center point _{O 3} of the actuator ring 11 The angle α formed by the angle is set to 60 to 100 °. By setting such an angle, even when a force in a direction in which the actuator ring 11 gets over the guide roller 13a or 13b is applied when the actuator ring 11 is rotated, the weight of the actuator ring is won and the guide rollers 13a and 13b The actuator ring 11 can be stably supported.

  In addition, the surface pressure applied to the guide rollers 13 a and 13 b by the weight of the actuator ring 11 can be reduced, and the driving force required for the actuator 10 to rotate the actuator ring 11 in the circumferential direction can be reduced.

  FIG. 2 shows an enlarged view of the guide roller 13a or 13b. In FIG. 2, the guide roller 13 a or 13 b is such that the rotation shaft 18 a of the roller 18 is rotatably supported by a bearing 19. The bearing 19 is fixed to the fixed portion 20.

  In such a configuration, the outer peripheral surface of the actuator ring 11 is supported by the two guide rollers 13 a and 13 b, the second guide roller 15 is applied to the inner peripheral surface of the actuator ring 11, and the actuator ring 11 is elastically applied to the spring member 16. Therefore, it is possible to eliminate play in the support portion of the actuator ring 11.

Therefore, when the actuator ring 11 is rotated in the direction of the arrow a or the arrow b by the actuator 10, the actuator ring 11 is only rotated and no extra revolving motion is caused. Therefore, the guide rollers 13a and 13b of the actuator ring 11 are not caused. Alternatively, the impact force does not act on the second guide roller 15 or the actuator 10. Therefore, these support mechanisms and actuators 10 can have a long life.
Further, since the discontinuous movement of the actuator ring 11 is eliminated, the angle error can be eliminated between the plurality of stationary blades. Therefore, the amount of air taken in from the air inlet i can be accurately controlled, thereby improving the thermal efficiency.

Further, since the actuator ring 11 is supported only by the two guide rollers 13a and 13b and the second guide roller 15, the support mechanism can be simplified.
In the present embodiment, a guide roller other than the guide rollers 13a and 13b may be disposed, for example, on the side or above the actuator ring 11 in order to ensure stable support of the actuator ring 11.

(Embodiment 2)
Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 3 is an enlarged view of the guide roller corresponding to FIG. In FIG. 3, the guide roller mechanism 30 according to the present embodiment is composed of two rollers 31 and 32 spaced apart from each other. The rotating shafts 31a and 32a of the rollers 31 and 32 are connected by a connecting rod 33 and supported by the connecting rod 33 so as to be rotatable.

  The intermediate portion of the connecting rod 33 is supported by the bearing 19, and the connecting rod 33 is pivotally attached to the bearing 19 via the rotating shaft 34. The bearing 19 is fixed to the fixed portion 20. Since other configurations are the same as those of the first embodiment, description thereof is omitted.

  According to this embodiment, since the guide roller mechanism 30 is constituted by the two rollers 31 and 32, the surface pressure of the actuator ring 11 applied to one roller can be reduced. Further, since the connecting rod 33 is rotatable with respect to the bearing 19, the surface pressure acting on the pair of rollers 31, 32 can be divided evenly. Design with is possible.

(Embodiment 3)
Next, a third embodiment of the present invention will be described with reference to FIG. 4, the actuator ring 11, supported by two guide rollers 13a and 13b arranged outside below the actuator ring 11, the central point _{O 1} of the actuator ring 11 and the guide roller 13a or 13b the central point _{O 2} or The angle α formed by the center lines L ₁ and L ₂ connecting O ₃ is the same as the angle α of the first embodiment.

  In the present embodiment, the drive mechanism that rotates the actuator ring 11 in the circumferential direction is different from that of the first embodiment. Hereinafter, the drive mechanism 40 of this embodiment will be described. Two brackets 41 and 42 are fixed to the lower outer peripheral surface of the actuator ring 11, and both ends of the chain belt 43 are connected to the brackets 41 and 42. A pulley 44 is disposed between the outer peripheral surface of the actuator ring 11 and the chain belt 43. The outer peripheral surface of the pulley 44 has an uneven portion 44 a that meshes with the uneven portion 43 a of the chain belt 43.

The uneven portion 44a of the pulley 44 meshes with the uneven portion 43a of the chain belt 43, and the chain belt 43 is rotated by rotating the pulley 44 in the forward or reverse direction (arrow a direction or arrow b direction) with a driving device (not shown). Can be pulled in the direction of arrow a or b.
Further, the pulley 44 is connected to the fixed portion 46 via the spring member 45, and the elastic force of the spring member 45 that biases the pulley 44 downward is applied to the pulley 44.

  In this configuration, the elastic force of the spring member 45 that pulls the chain belt 43 downward is applied to the chain belt 43 via the pulley 44. Therefore, the chain belt 43 always applies an elastic force that presses the actuator ring 11 against the guide rollers 13a and 13b. In this state, when the pulley 44 is rotated in the forward or reverse direction by a driving device (not shown), a tensile force is applied to the chain belt 43 in the direction of arrow a or arrow b, and the actuator ring 11 is moved in the direction of arrow a or arrow. It can be rotated in the b direction.

According to the present embodiment, since the elastic force that always presses the actuator ring 11 against the guide rollers 13a and 13b is applied, no play occurs between the actuator ring 11 and the guide rollers 13a or 13b. Sometimes, the impact force does not act on the guide rollers 13a and 13b, the chain belt 43 and the pulley 44. Therefore, the lifetime of these devices can be improved without causing damage or cracking of these devices.
Further, since the actuator ring 11 does not move discontinuously, no angular error occurs between the plurality of variable stationary blades. Therefore, since the air intake amount can be accurately controlled, the thermal efficiency can be improved.

  Further, since the support mechanism and the drive mechanism of the actuator ring 11 are constituted by the two guide rollers 13a and 13b, the chain belt 43, the pulley 44, etc., the support mechanism and the drive mechanism can be simplified, and these Since the device is not disposed at the air intake i inside the actuator ring 11, there is no possibility of generating an air flow.

In the third embodiment, instead of using the chain belt 43, the rotational force of the pulley 44 may be transmitted to the actuator ring 11 using a steel belt, a link mechanism, or the like.
The first to third embodiments are examples in which the present invention is applied to variable inlet guide vanes of a gas turbine compressor. However, the present invention is not limited to variable inlet guide vanes, and other variable stationary vanes. Applicable in general.

  ADVANTAGE OF THE INVENTION According to this invention, the variable mechanism of the stationary blade provided in the axial flow compressor can be extended in life and simplified, and the operation of the variable stationary blade can be accurately controlled.

It is a typical front view of the variable stationary blade drive device concerning a 1st embodiment of the present invention. It is an enlarged view of the guide roller of the apparatus in FIG. It is an enlarged view of the guide roller which concerns on 2nd Embodiment of this invention. It is a typical front view of the variable stationary blade drive device which concerns on 3rd Embodiment of this invention. It is a perspective view of the conventional variable stationary blade drive device. It is a perspective view of another conventional variable stationary blade drive device. It is operation | movement explanatory drawing of the variable stationary blade drive device of FIG.

Explanation of symbols

02, 012 Variable stator blade 05 Driving force transmission mechanism 10 Actuator 11 Actuator ring 13a, 13b Guide roller 15 Second guide roller 16 Spring member (elastic force addition mechanism)
19 Bearing (support)
31, 32 Roller 33 Connecting rod 40 Actuator ring drive mechanism 43 Chain belt (rotating force addition belt)
44 Pulley (belt car)
45 Spring member (spring mechanism)
i Air intake (fluid flow path)
L ₁ , L ₂ center line

Claims (6)

An axial flow compressor that rotates a ring supported rotatably along a plurality of variable stator blades arranged in an annular shape surrounding a fluid flow path, and rotates the variable stator blades via a driving force transmission mechanism. In the variable vane driving method,
With the ring standing up and down, it is placed on and supported by two guide rollers that are smaller than the diameter of the ring and have an interval that enables stable support of the ring and is arranged below the ring,
An elastic force is applied to the ring in a direction in which the ring is pressed against the guide roller,
In this state, the ring is rotated in the circumferential direction to change the direction of the stationary blades. A ring that is rotatably supported along a plurality of variable stator vanes that are annularly arranged around the fluid flow path, an actuator that rotates the ring in the forward or reverse direction in the circumferential direction, and a movement of the ring. In a variable stator blade drive device of an axial compressor having a driving force transmission mechanism that transmits to a variable stator blade,
Two guide rollers that support the ring in an upright direction, and that are smaller than the diameter of the ring and arranged below the ring with a spacing that enables stable support of the ring;
An elastic force application mechanism that applies an elastic force in a direction of pressing the ring against the guide roller,
A variable stator blade drive device for an axial compressor, wherein the ring is rotated in the circumferential direction by the actuator while the ring is pressed against the guide roller by the elastic force applying mechanism. The elastic force applying mechanism is supported on the inner side of the ring via a spring member, pressed against the inner peripheral surface of the ring by the elastic force of the spring member, and elastic in the direction of pressing the ring against the guide roller. The variable stationary blade drive device for an axial compressor according to claim 2, wherein the variable guide blade drive device is configured by a second guide roller for applying a force.   The elastic force applying mechanism is arranged between the ring and the rotational force applying belt, which is disposed between the ring and the rotational force applying belt, and rotates around the ring. The belt wheel that is rotated in a direction and a spring mechanism that applies an elastic force in a direction that tensions the belt that adds a rotational force downward with respect to the belt wheel. Variable stator vane drive unit for axial compressor.   The stator blade of an axial compressor according to claim 2, wherein an angle formed by two center lines connecting the center of the ring and the centers of the two guide rollers is 60 to 100 °. Drive device.   The guide roller is composed of two rollers that are rotatably connected by a connecting rod, and an intermediate portion of the connecting rod is pivotally attached to a support portion, and the two rollers are used as a ring. The variable stator vane drive device for an axial compressor according to claim 2, wherein the load is uniformly loadable.

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