CN220336953U - Linkage ring centering structure and gas turbine thereof - Google Patents

Abstract

The application discloses a linkage ring centering structure and gas turbine thereof, and relates to the technical field of gas turbines. The linkage ring centering structure includes: the linkage ring is used for being movably sleeved with the compressor case; the rolling assemblies are used for being arranged on the outer wall of the compressor box; each rolling assembly is uniformly arrayed around the axial lead of the compressor box; the outer wall of each rolling assembly is in contact with the inner wall of the linkage ring; each rolling assembly is capable of central rotation about a first axis, and the first axis is parallel to the axis of the coupling ring. The application can support the linkage ring through the rolling assembly to the friction that forms between rolling assembly and the linkage ring is rolling friction, for sliding friction, rolling friction's wearing and tearing are less. That is, the rolling assembly is not easily worn, and does not need to be replaced frequently, so that the use cost can be reduced.

Description

Linkage ring centering structure and gas turbine thereof

Technical Field

The application relates to the technical field of gas turbines, in particular to a linkage ring centering structure and a gas turbine thereof.

Background

In order to meet the requirements of high efficiency and high margin of a gas turbine compressor, a stator blade angle adjusting structure is generally designed when the compressor is designed. The stator blade angle adjusting structure is mainly used for adjusting the angle of the stator blade in the compressor so as to meet the pneumatic performance of the compressor at different rotating speeds. Specifically, the angle adjusting structure of the stator blade in the prior art is shown in fig. 1 and 2, and comprises a linkage ring 2 and a Z-shaped connecting rod 3 corresponding to a plurality of stator blades 4 one by one. The linkage ring 2 is movably sleeved outside the compressor case 1. The plurality of stator blades 4 are uniformly distributed along the circumferential direction of the compressor casing 1, and each stator blade 4 can be rotationally connected with the compressor casing 1. One end of the Z-shaped connecting rod 3 is hinged with the linkage ring 2, and the other end of the Z-shaped connecting rod 3 is fixed with the stator blade 4. If the linkage ring 2 is rotated, the linkage ring 2 can drive each stator blade 4 to synchronously rotate through each Z-shaped connecting rod 3.

It is clear that the angle control precision of the stator blades of the same circle on the compressor box has great influence on the stable operation of the compressor in the operation process of the compressor. In the prior art, for convenient assembly, the linkage ring is generally formed by connecting two semi-rings, and the linkage ring is generally thinner and narrower in axial width, so that the rigidity of the linkage ring is poorer, and the concentricity of the linkage ring and the compressor casing is harder to ensure in the working and rotating processes of the assembly and the linkage ring. That is, the compressor is unstable due to inconsistent angle control precision of the stator blades of the same circle on the compressor box in the working process of the compressor. In order to solve the above-mentioned problems, as shown in fig. 1 and 2, a stop collar 5 is generally disposed between the compressor casing 1 and the linkage ring 2 as a stop device of the linkage ring 2 to control concentricity of the linkage ring 2 and the compressor casing 1, thereby ensuring the consistency of the angular rotation of the stator blades. But can produce sliding friction between linkage ring and the stop collar, lead to the stop collar wearing and tearing relatively easily, need often change, increase use cost.

Disclosure of Invention

The utility model aims at providing a linkage ring centering structure and gas turbine thereof to solve among the prior art stop collar and wear easily, lead to often changing, increase use cost's technical problem.

In order to achieve the above purpose, the present application provides the following technical solutions:

in a first aspect, the present application proposes a ganged ring centering structure comprising: the linkage ring is used for being movably sleeved with the compressor case; the rolling assemblies are used for being arranged on the outer wall of the compressor box; each rolling assembly is uniformly arrayed around the axial lead of the compressor box; the outer wall of each rolling assembly is in contact with the inner wall of the linkage ring; each rolling assembly is capable of central rotation about a first axis, and the first axis is parallel to the axis of the coupling ring.

As one implementation in the examples of this application, the rolling assembly includes: the fixed shaft is fixedly connected with the compressor box; and the rotating sleeve is movably sleeved outside the fixed shaft.

As an implementation manner in the embodiment of the present application, the rolling assembly further includes a limiting member disposed on the fixed shaft, where the limiting member is configured to limit relative displacement between the rotating sleeve and the fixed shaft along a first direction, and the first direction is parallel to an axial line of the fixed shaft.

As one implementation mode in this application embodiment, the locating part includes two stoppers, the cover that rotates is located between two stoppers, just the length of cover along the first direction is not greater than the interval along the first direction of two stoppers.

As an implementation mode in this application embodiment, the fixed axle includes the axle body, the through-hole has been seted up at the both ends of axle body, the axle body through-hole and bolt with the compressor casket screw thread is fixed.

As one implementation in the examples of this application, the fixed axle includes: a shaft body; the two supporting blocks are respectively arranged at two ends of the shaft body, each supporting block comprises a through hole, and the supporting blocks are fixed with the compressor box through the through holes and bolts in a threaded mode.

As one implementation in the examples of this application, the fixed axle includes: a shaft body; the two elastic pieces are respectively arranged at two ends of the shaft body and are fixed with the compressor box; the elastic piece is used for applying elastic force parallel to the second direction to the shaft body; the second direction is parallel to the radial direction of the compressor case and is directed outward from the inside of the compressor case.

As an implementation manner in the embodiment of the application, the elastic piece includes a spring, or the elastic piece includes an elastic rod and a connecting piece, the connecting piece is disposed at one end of the elastic rod, and the other end of the elastic rod is connected with the end of the shaft body.

As one implementation mode of the embodiment of the application, an included angle formed by the axial lead of the elastic rod and the axial lead of the shaft body is more than or equal to 90 degrees and less than or equal to 150 degrees.

In a second aspect, the present application proposes a gas turbine comprising a plurality of ganged-ring centering structures as set forth in any one of the first aspects.

Compared with the prior art, the beneficial effects of this application are:

the linkage ring can be supported by the rolling assembly, and friction formed between the rolling assembly and the linkage ring is rolling friction, and relative to sliding friction, the abrasion of the rolling friction is small. That is, the rolling assembly is not easily worn, and does not need to be replaced frequently, so that the use cost can be reduced.

Drawings

FIG. 1 is a perspective view of a prior art linkage ring and compressor case connection as set forth in the present application;

FIG. 2 is a front view of FIG. 1;

fig. 3 is a perspective view of a linkage ring and compressor case connection (via a rolling assembly) according to an embodiment of the present application;

FIG. 4 is a front view of FIG. 3;

FIG. 5 is a perspective view of a rolling assembly according to an embodiment of the present application;

fig. 6 is a cross-sectional view of the connection of the rolling assembly with the compressor case of fig. 5;

FIG. 7 is a perspective view of a stationary shaft according to an embodiment of the present application;

FIG. 8 is a perspective view of another stationary shaft according to an embodiment of the present application;

FIG. 9 is a perspective view of yet another stationary shaft according to an embodiment of the present application;

fig. 10 is a front view of fig. 9.

In the figure: 1. a compressor case; 2. a linkage ring; 3. a Z-shaped connecting rod; 4. stator blades; 5. a limit sleeve; 6. a rolling assembly; 610. a fixed shaft; 611. a shaft body; 612. a through hole; 613. a support block; 614. an elastic rod; 615. a connecting sheet; 620. a rotating sleeve; 630. a limiting block; 640. and (5) a bolt.

Detailed Description

The following description of the embodiments of the present application will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all, of the embodiments of the present application. All other embodiments, which can be made by one of ordinary skill in the art without undue burden from the present disclosure, are within the scope of the present disclosure.

It should be noted that, in the description of the present application, the terms "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like indicate an orientation or a positional relationship based on that shown in the drawings, which are merely for convenience of description and simplification of the description, and do not indicate or imply that the apparatus or element to be referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present application.

Furthermore, it should be understood that the dimensions of the various elements shown in the figures are not drawn to actual scale, e.g., the thickness or width of some layers may be exaggerated relative to other layers for ease of description.

It should be noted that like reference numerals and letters refer to like items in the following figures, and thus once an item is defined or illustrated in one figure, no further detailed discussion or description thereof will be necessary in the following description of the figures.

In order to solve the technical problem proposed in the background art, the application provides a linkage ring centering structure. As shown in fig. 3 and 4, the interlock ring centering structure includes an interlock ring 2 and a plurality of rolling assemblies 6 provided to an outer wall of the compressor case 1.

Specifically, the linkage ring 2 is movably sleeved outside the compressor casing 1, that is, the linkage ring 2 can rotate around the axial lead of the compressor casing 1, so as to adjust the angle of the stator blade 4 through the Z-shaped connecting rod 3. As shown in fig. 3 and 4, a plurality of rolling assemblies 6 are uniformly arrayed around the axial line of the compressor case 1. The outer wall of each rolling assembly 6 abuts against the inner wall of the linkage ring 2. It should be clear that in the embodiments of the present application, the rolling assemblies 6 are made to collide with the coupling ring 2 in order to avoid a gap between the outer wall of the rolling assemblies 6 and the inner wall of the coupling ring 2, so as to prevent the coupling ring 2 from being not coaxial with the compressor case 1 when rotating. That is, there is a certain interference force between the outer wall of the rolling assembly 6 and the inner wall of the coupling ring 2, and the interference force may be any value greater than or equal to 0. In the embodiment of the application, the magnitude of the interference force can be reasonably controlled by adjusting the tightness degree of the linkage ring 2 during installation according to actual requirements. It should be noted that in the embodiments of the present application, each rolling assembly 6 is capable of central rotation about a first axis, which is parallel to the axis of the linkage ring 2.

In particular, in the embodiments of the present application, if the rolling element 6 is similar to the bearing structure presented below, the first axis is the axis of the rolling element 6; if the rolling assembly 6 is similar to the ball structure presented below, the first axis passes through the centre of gravity of the balls.

It will be readily appreciated that the rolling assembly 6 is capable of central rotation about the first axis. In other words, the friction generated between the coupling ring 2 and the rolling assembly 6 is rolling friction. Compared with the sliding friction force, the rolling friction force has less abrasion on the rolling assembly 6, so that the rolling assembly 6 can be used for a long time without frequent replacement, and the use cost can be effectively reduced.

Specifically, in the embodiment of the present application, the rolling assembly 6 may be any structure capable of performing a central rotation about its own axis. For example: the rolling assembly 6 may be similar to a bearing structure, a ball structure, or as shown in fig. 5, the rolling assembly 6 includes a stationary shaft 610 and a rotating sleeve 620. The fixed shaft 610 is fixedly connected with the compressor case 1, and the rotating sleeve 620 is movably sleeved outside the fixed shaft 610. That is, the rotating sleeve 620 can perform a central rotation on the fixed shaft 610 about the axial line of the fixed shaft 610. It is readily understood that in embodiments of the present application, the rotating sleeve 620 may be a bearing, although in other embodiments of the present application, as shown in fig. 6, the rotating sleeve 620 may be a tubular sleeve structure.

It should be clear that, in order to avoid the relative displacement between the rotating sleeve 620 and the fixed shaft 610 in the first direction when the rotating sleeve 620 rotates in the center, the rolling assembly 6 further includes a limiting member disposed on the fixed shaft 610, where the limiting member is used to limit the relative displacement between the rotating sleeve 620 and the fixed shaft 610 in the first direction, and the first direction is parallel to the axis of the fixed shaft 610.

Specifically, in the embodiment of the present application, the limiting member may be any component capable of limiting the axial movement of the rotating sleeve 620. For example: springs may be provided at both ends of the rotating sleeve 620, the springs being coupled with the fixed shaft 610 and storing elastic potential energy, or as shown in fig. 5 and 6, the stopper includes two stoppers 630, and the rotating sleeve 620 is positioned between the two stoppers 630.

It should be clear that in the embodiment of the present application, the shape and configuration of the stopper 630 are not limited at all, as long as it can play a role of stopper. For example: in one embodiment of the present application, as shown in fig. 5 and 6, the limiting block 630 may be in a circular block shape, and in other embodiments of the present application, the limiting block 630 may also be in a square block shape, a triangular block shape, or a rod shape. It should be noted that, in the embodiment of the present application, as shown in fig. 6, the length of the rotating sleeve 620 along the first direction may be equal to the spacing between the two limiting blocks 630 along the first direction. At this time, the two limiting blocks 630 can perform a better limiting function on the rotating sleeve 620. It should be clear that, during the rotation of the linkage ring 2, if the friction force generated between the linkage ring 2 and the rolling assemblies 6 is smaller than the resistance of the rolling assemblies 6 to perform the central rotation, the rolling assemblies 6 cannot perform the central rotation around the first axis, that is, if the resistance of the rolling assemblies 6 to perform the central rotation is too large, the rolling friction is difficult to be formed between the rolling assemblies 6 and the linkage ring 2. In other words, when designing the rolling assembly 6, the resistance to the center rotation of the rolling assembly 6 should be reduced as much as possible. Considering errors in the production process and expansion and contraction during use, if the length of the rotating sleeve 620 along the first direction is equal to the distance between the two limiting blocks 630 along the first direction, the two limiting blocks 630 easily block the rotating sleeve 620 from rotating in the center, that is, easily increase the resistance of the rotating sleeve 620 when rotating in the center. In one embodiment of the present application, to reduce the resistance of the rotation sleeve 620 to center rotation, the length of the rotation sleeve 620 along the first direction may be smaller than the spacing between the two stoppers 630 along the first direction.

In the embodiment of the present application, the fixed shaft 610 may be a shaft of any shape or configuration, without any limitation. As shown in fig. 7, the fixed shaft 610 may include only the shaft body 611, and the shaft body 611 may be directly welded to the outer wall of the compressor case 1 when in use. In one embodiment of the present application, in order to facilitate the disassembly and assembly of the rolling assembly 6, as shown in fig. 7, through holes 612 are formed at both ends of the shaft body 611, and the shaft body 611 is screw-fastened to the compressor case 1 through the through holes 612 and bolts 640.

It should be clear that the outer surface of the shaft body 611 has an arc, and the outer surface of the compressor case 1 also has an arc, that is, the contact area formed between the shaft body 611 and the compressor case 1 is small. The shaft body 611 (i.e. the fixed shaft 610) is directly screwed with the compressor casing 1 through the bolt 640, and the fixed shaft 610 and the compressor casing 1 are easy to loosen during long-term use. In order to enable the fixed shaft 610 to be better connected with the compressor case 1, looseness is not easily generated, and in one embodiment of the present application, as shown in fig. 8, the fixed shaft 610 includes a shaft body 611 and two supporting blocks 613. The two supporting blocks 613 are respectively disposed at two ends of the shaft body 611, and the supporting blocks 613 are used for increasing a contact area formed between the fixed shaft 610 and the compressor casing 1, so that the fixed shaft 610 is connected with the compressor casing 1 more stably. It is of course conceivable to provide the support block 613 with an inner concave surface adapted to the outer surface of the compressor casing 1, in order to increase the contact area of the support block 613 with the compressor casing 1.

It should be clear that the shape and the configuration of the support block 613 are not limited in the embodiment of the present application as long as the contact area of the shaft body 611 and the compressor case 1 can be increased. For example: in one embodiment of the present application, the support block 613 may be square as shown in fig. 8, or sheet like as shown in fig. 9 similar to the connecting sheet 615.

Specifically, in the embodiment of the present application, the supporting blocks 613 may be welded or riveted with the compressor casing 1, and as shown in fig. 6 and 8, a through hole 612 may be formed in each supporting block 613, and the supporting blocks 613 may be screwed with the compressor casing 1 through the through holes 612 and the bolts 640.

As can be seen from the foregoing, in the embodiment of the present application, a certain interference force is required between the rotating sleeve 620 and the linkage ring 2, so that the rotating sleeve 620 can perform a better supporting function on the linkage ring 2. Although the friction between the rotating sleeve 620 and the link ring 2 is sliding friction, wear may still occur to the rotating sleeve 620 and/or the link ring 2 during long-term use in order to provide sufficient interference between the rotating sleeve 620 and the link ring 2. As shown in fig. 9, the fixed shaft 610 includes a shaft body 611 and two elastic members. The two elastic members are respectively disposed at two ends of the shaft body 611, and the elastic members are fixed with the compressor case 1. The elastic member is used to apply an elastic force parallel to the second direction to the shaft body 611; the second direction is parallel to the radial direction of the compressor case 1 and is directed outward from the inside of the compressor case 1. That is, after the installation of the link ring 2 is completed, the elastic member can provide a sufficient interference force between the rotating sleeve 620 and the link ring 2 through the shaft body 611. Even after wear of the rotating sleeve 620 and/or the linkage ring 2, the rotating sleeve 620 is enabled to support the linkage ring 2.

In particular, in embodiments of the present application, the elastic member may be a spring. When the arrangement is made, the axial line of the spring is parallel to the radial direction of the compressor case 1. In another embodiment of the present application, as shown in fig. 9 and 10, the elastic member includes an elastic rod 614 and a connection piece 615, the connection piece 615 is disposed at one end of the elastic rod 614, and the other end of the elastic rod 614 is connected to an end of the shaft body 611. The function of the tab 615 in the embodiments of the present application is similar to that of the support block 613 above. The elastic rod 614 has elasticity, and can generate elastic force after the elastic rod 614 is subjected to bending deformation.

It should be clear that, as shown in fig. 10, in one embodiment of the present application, the axial line of the elastic rod 614 (shown as a line segment B in fig. 10) forms an angle C with the axial line of the shaft body 611 (shown as a line segment a in fig. 10), and the angle C may be 90 °. As can be seen from the foregoing, the elastic rod 614 is bent and deformed to generate elastic force. If the angle C is 90 °, the elastic rod 614 is not easily bent when the coupling ring 2 is attached. To facilitate bending of the resilient lever 614 to deform the resilient lever 614, in another embodiment of the present application, the angle C is greater than 90.

It should be clear that the amount of elastic force generated by the elastic rod 614 is equal to the elastic coefficient of the elastic rod 614 multiplied by the amount of deformation of the elastic rod 614. That is, if the elastic rod 614 is required to generate a sufficient elastic force, the elastic rod 614 is required to generate a sufficient amount of deformation. As shown in fig. 10, when the angle C is close to 180 °, the amount of deformation that can be generated by the elastic lever 614 is extremely small, that is, the elastic force that can be generated by the elastic lever 614 is also extremely small. In the embodiment of the present application, in order to ensure that the elastic rod 614 is capable of generating a sufficient amount of deformation, the angle C is 150 ° or less.

Specifically, in the embodiment of the present application, the angle C may be any one degree of 90 °, 100 °, 110 °, 120 °, 130 °, 140 ° and 150 °, and of course, in other embodiments of the present application, the angle C may also be any degree between the two adjacent degrees.

According to the linkage ring centering structure, the linkage ring can be supported through the rolling assembly, friction formed between the rolling assembly and the linkage ring is rolling friction, and abrasion of the rolling friction is small relative to sliding friction. That is, the rolling assembly is not easily worn, and does not need to be replaced frequently, so that the use cost can be reduced.

Having described all of the embodiments of the ganged-ring centering structure presented herein, a gas turbine, and in particular, a gas turbine, as presented herein, includes a plurality of ganged-ring centering structures as presented in any of the ganged-ring centering structure embodiments described above.

The gas turbine provided by the application is provided with the linkage ring centering structure provided in the embodiment of the application. That is, the gas turbine can support the linkage ring by the rolling assembly, and friction formed between the rolling assembly and the linkage ring is rolling friction, and abrasion of the rolling friction is small relative to sliding friction. That is, the rolling assembly is not easily worn, and does not need to be replaced frequently, so that the use cost can be reduced.

Although embodiments of the present application have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made therein without departing from the principles and spirit of the application, the scope of which is defined in the appended claims and their equivalents.

Claims (10)

1. A ganged-ring centering structure, comprising:

the linkage ring (2) is used for being movably sleeved with the compressor case (1);

the rolling assemblies (6) are arranged on the outer wall of the compressor box (1); and each rolling assembly (6) is uniformly arrayed around the axial lead of the compressor casing (1); the outer wall of each rolling assembly (6) is in contact with the inner wall of the linkage ring (2); each rolling assembly (6) is capable of centre rotation about a first axis, and the first axis is parallel to the axis of the linkage ring (2).

2. The ganged-ring centering structure of claim 1, characterized in that the rolling assembly (6) comprises:

the fixed shaft (610) is fixedly connected with the compressor box (1);

and the rotating sleeve (620) is movably sleeved outside the fixed shaft (610).

3. The ganged-ring centering structure of claim 2, characterized in that the rolling assembly (6) further comprises a stop provided to the stationary shaft (610) for limiting relative displacement between the rotating sleeve (620) and the stationary shaft (610) in a first direction, the first direction being parallel to an axis of the stationary shaft (610).

4. A linkage ring centering structure as claimed in claim 3, wherein the stop member comprises two stop blocks (630), the rotating sleeve (620) is located between the two stop blocks (630), and a length of the rotating sleeve (620) along the first direction is not greater than a distance between the two stop blocks (630) along the first direction.

5. The linkage ring centering structure according to any one of claims 2 to 4, wherein the fixed shaft (610) comprises a shaft body (611), through holes (612) are formed at both ends of the shaft body (611), and the shaft body (611) is screwed with the compressor case (1) through the through holes (612) and bolts (640).

6. The ganged-loop centering structure of any one of claims 2 to 4, characterized in that the fixed shaft (610) comprises:

a shaft body (611);

two supporting blocks (613) are respectively arranged at two ends of the shaft body (611), each supporting block (613) comprises a through hole (612), and the supporting blocks (613) are fixed with the compressor case (1) through the through holes (612) and bolts (640) in a threaded mode.

7. The ganged-loop centering structure of any one of claims 2 to 4, characterized in that the fixed shaft (610) comprises:

a shaft body (611);

the two elastic pieces are respectively arranged at two ends of the shaft body (611) and are fixed with the compressor case (1); the elastic member is used for applying elastic force parallel to a second direction to the shaft body (611); the second direction is parallel to the radial direction of the compressor case (1) and points outwards from the inside of the compressor case (1).

8. The linkage ring centering structure according to claim 7, wherein the elastic member includes a spring, or the elastic member includes an elastic rod (614) and a connecting piece (615), the connecting piece (615) is provided at one end of the elastic rod (614), and the other end of the elastic rod (614) is connected with an end of the shaft body (611).

9. The linkage ring centering structure according to claim 8, wherein an included angle formed by an axial line of the elastic rod (614) and an axial line of the shaft body (611) is greater than or equal to 90 ° and less than or equal to 150 °.

10. A gas turbine comprising a plurality of the ganged-ring centering structures as claimed in any one of claims 1 to 9.