WO2021039811A1 - Swirl breaker assembly and rotating machine - Google Patents

Abstract

A swirl breaker assembly according to one embodiment comprises: an annular body that extends along the circumferential direction; a flow guide that projects from the annular body in the axial direction, so as to extend along the circumferential direction; and a plurality of swirl breakers that are provided, with intervals therebetween in the circumferential direction, to the annular body at positions which are offset in the radial direction with respect to the flow guide.

Description

Swirl breaker assembly and rotating machine

This disclosure relates to swirl breaker assemblies and rotary machines.

Rotating machines such as steam turbines and gas turbines used in power plants are known. This rotating machine has moving blades supported by a turbine rotor (hereinafter, simply referred to as a rotor) that is rotatable with respect to the casing, and stationary blades supported by the casing, and is upstream to downstream in the axial direction of the rotor. It is configured to convert the energy of the working fluid flowing into the rotor into the rotational energy of the rotor.

In the rotary machine, in the seal portion that seals between the rotor or the moving blade and the casing, the working fluid deviating from the main flow path flows in while having the swirling flow component given when it passes through the nozzle. It is known that a swirling flow (so-called swirl flow) is generated in the circumferential direction of the rotor. When the rotor is eccentric due to the swirl flow, a sinusoidal pressure distribution having a peak in a direction different from the eccentric direction of the rotor is generated in the circumferential direction of the rotor, and the swirl flow increases with high output operation, for example. In some cases, it may cause self-excited vibration of the rotor. For this reason, various structures for suppressing the swirl flow in the seal portion have been devised. For example, in Patent Document 1, a turbine is provided in a stationary portion that opposes a portion on the tip side of a turbine moving blade in the axial direction of a rotating machine. A structure provided with a plurality of protrusions (rectifying portions) protruding toward the moving blade side is disclosed (see Patent Document 1).

Japanese Unexamined Patent Publication No. 2008-184974

In recent years, in rotary machines such as steam turbines and gas turbines, in order to improve turbine efficiency, the rotor diameter tends to be smaller and the blades tend to be multistage. Therefore, since the rotor has a smaller diameter and a longer shaft, self-excited vibration of the rotor tends to occur easily. Therefore, there is a need for a countermeasure plan for more effectively suppressing self-excited vibration.

In view of the above circumstances, at least one embodiment of the present invention aims to suppress the occurrence of self-excited vibration in a rotating machine.

(1) The swirl breaker assembly according to at least one embodiment of the present invention is
An annular body that extends along the circumferential direction,
A flow guide that projects axially from the annular body so as to extend along the circumferential direction.
A plurality of swirl breakers provided on the annular body at positions displaced in the radial direction with respect to the flow guide at intervals in the circumferential direction.
To be equipped.

Consider a case where the swirl breaker assembly having the above configuration (1) is arranged as follows, for example, on the upstream side of the rotor blade of the rotary machine. That is, the swirl breaker assembly having the configuration of (1) above is arranged so that, for example, the flow guide projects radially inward from the outer peripheral surface of the outer shroud in the radial direction so as to project toward the downstream side in the axial direction. Further, the swirl breaker assembly having the configuration of (1) above is arranged so that, for example, a plurality of swirl breakers project radially outward from the flow guide to the downstream side in the axial direction.
For example, in a rotating machine such as a steam turbine, a working fluid deviating from the main flow path flows into the space between the outer shroud and the inner peripheral surface of the casing of the rotating machine while having a swirling flow component as described above.
When the swirl breaker assembly having the configuration of (1) above is arranged in the rotating machine as described above, the working fluid deviating from the main flow path flows into the space from the main flow path on the radial outer surface of the flow guide. You will be guided along to multiple swirl breakers. That is, according to the configuration of (1) above, the working fluid deviated from the main flow path can be efficiently guided to the swirl breaker. As a result, the swirling flow component of the working fluid deviated from the main flow path can be efficiently suppressed by the plurality of swirl breakers, so that the self-excited vibration of the rotor due to the swirl flow can be efficiently suppressed.

(2) In some embodiments, in the configuration of (1) above, the plurality of swirl breakers have their radial ends connected to the flow guide.

When the end of the plurality of swirl breakers is not connected to the flow guide, a part of the working fluid deviating from the main flow path will flow in the circumferential direction from between the end and the flow guide, and the end Compared with the case where the part and the flow guide are connected, the effect of suppressing the swirling flow component by the swirl breaker is reduced.
On the other hand, according to the configuration of (2) above, the effect of suppressing the swirling flow component by the swirl breaker is enhanced. Further, according to the configuration of (2) above, the projected area of the swirl breaker when viewed from the circumferential direction can be increased, and the effect of suppressing the swirling flow component by the swirl breaker is enhanced.

(3) In some embodiments, in the configuration of (1) or (2) above, the plurality of swirl breakers overlap the flow guide at least partially in the axial direction.

According to the configuration of (3) above, since the plurality of swirl breakers overlap with the flow guide in the axial direction, the working fluid deviating from the main flow path is efficiently guided to the swirl breaker by the flow guide.

(4) In some embodiments, in any of the configurations (1) to (3), the flow guide has the axial position of the axially protruding end along the axial direction. It exists between the base end portion and the tip end portion of the plurality of swirl breakers.

According to the configuration (4) above, the axial position of the flow guide with respect to the protruding end exists between the base end portion and the tip end portion of the plurality of swirl breakers along the axial direction, so that the main flow path The working fluid deviated from the flow guide is efficiently guided to the swirl breaker by the flow guide.

(5) In some embodiments, in any of the configurations (1) to (4), the flow guide has a guide surface that points to the plurality of swirl breaker sides in the radial direction.

According to the configuration of (5) above, the working fluid deviating from the main flow path is efficiently guided to the swirl breaker by the guide surface.

(6) In some embodiments, in the configuration of (5) above,
The annular body has an annular body-side facing wall surface that faces the guide surface in the radial direction, and an annular body side wall surface that connects the guide surface and the annular body-side facing wall surface.
The plurality of swirl breakers exist in the space between the guide surface, the annular side wall surface, and the annular body side facing wall surface.

According to the configuration of (6) above, the working fluid deviating from the main flow path is guided to the space by the flow guide. Then, the swirling flow component of the working fluid guided to the space is suppressed by the plurality of swirl breakers existing in the space. As a result, the effect of suppressing the swirling flow component by the swirl breaker is enhanced.

(7) In some embodiments, in any of the configurations (1) to (6), the plurality of swirl breakers have seal fins having a tip portion along the axial direction extending in the circumferential direction. Is connected to.

When the tips of the plurality of swirl breakers are not connected to the seal fins extending in the circumferential direction, a part of the working fluid deviating from the main flow path is circumferentially from between the tips and the seal fins. Since the fluid flows, the effect of suppressing the swirling flow component by the swirl breaker is reduced as compared with the case where the tip portion and the seal fin are connected.
On the other hand, according to the configuration of (7) above, the effect of suppressing the swirling flow component by the swirl breaker is enhanced. Further, according to the configuration of (7) above, the projected area of the swirl breaker when viewed from the circumferential direction can be increased, and the effect of suppressing the swirling flow component by the swirl breaker is enhanced.

(8) In some embodiments, in any of the configurations (1) to (7) above, the plurality of swirl breakers have a plate shape extending along the axial direction and the radial direction.

According to the configuration of (8) above, since the shape of the plurality of swirl breakers is a simple shape, it is easy to form.

(9) In some embodiments, in any of the configurations (1) to (8), the plurality of swirl breakers gradually increase in size in the circumferential direction toward the proximal end in the axial direction. It has a shape that widens the hem.

According to the configuration of (9) above, the circumferential dimension of the swirl breaker on the proximal end side in the axial direction is increased, so that the bending strength of the swirl breaker in the circumferential direction is improved. Further, since the shape of the swirl breaker on the base end side is a hem-spreading shape, it becomes easy to form the swirl breaker when the swirl breaker is formed by, for example, cutting out in the annular body.

(10) In some embodiments, in any of the configurations (1) to (9), the plurality of swirl breakers are said to be said when viewed in the radial direction in a region on the tip side in the axial direction. The flow guide side is thinner in the circumferential direction.

Consider a case where the swirl breaker assembly having the above configuration (10) is arranged as follows, for example, on the upstream side of the rotor blade of the rotary machine. That is, the swirl breaker assembly having the configuration (10) is arranged so that, for example, the flow guide projects radially inward from the outer peripheral surface of the outer shroud in the radial direction so as to project toward the downstream side in the axial direction. Further, the swirl breaker assembly having the configuration of (10) above is arranged so that, for example, a plurality of swirl breakers project radially outward from the flow guide.
When the swirl breaker assembly having the configuration of the above (10) is arranged on the rotating machine as described above, in the swirl breaker, the part on the flow guide side moves when viewed in the radial direction in the region on the tip side in the axial direction. It is located near the radial outer end of the blade. Therefore, there is a possibility that the portion and the radial outer end of the rotor blade come into contact with each other due to heat expansion or the like due to the operation of the rotating machine.
According to the configuration of (10) above, as compared with the case where the thickness of the portion in the circumferential direction is the same as that of the other portions, the portion and the radial outer end of the rotor blade come into contact with each other. Even if it does, the influence on the moving blades can be suppressed.

(11) In some embodiments, in any of the configurations (1) to (10), the plurality of swirl breakers are provided at equal intervals in the circumferential direction.

When the amount of working fluid sent into the rotating machine fluctuates, the flow of working fluid deviating from the main flow path also changes, so it is better than arranging multiple swirl breakers provided in the annular body unevenly along the circumferential direction. It is desirable to arrange them evenly. Therefore, according to the configuration of (11) above, the arrangement position along the circumferential direction in the plurality of swirl breakers is appropriate.

(12) The rotary machine according to at least one embodiment of the present invention is
With the swirl breaker assembly having any of the above configurations (1) to (11),
A rotor disc that rotates around the axis in the casing,
A plurality of rotor blade bodies attached to the rotor disk,
An outer shroud connected to the tip of each of the plurality of rotor blade bodies,
To be equipped.

According to the configuration of the above (12), since the swirl breaker assembly having the configuration of any one of the above (1) to (11) is provided, the self-excited vibration of the rotor due to the swirl flow can be efficiently suppressed.

(13) In some embodiments, in the configuration of (12) above,
The flow guide protrudes toward the downstream side in the axial direction on the upstream side in the axial direction from the rotor blade body and on the inner side in the radial direction from the outer peripheral surface on the radial outer side of the outer shroud.
The plurality of swirl breakers project outward in the radial direction from the flow guide to the downstream side in the axial direction.

According to the configuration (13) above, when the working fluid deviating from the main flow path flows from the main flow path into the space between the outer shroud and the inner peripheral surface of the casing of the rotating machine, the radial outer surface of the flow guide You will be guided to multiple swirl breakers along. That is, according to the configuration (13) above, the working fluid deviated from the main flow path can be efficiently guided to the swirl breaker. As a result, the swirling flow component of the working fluid deviated from the main flow path can be efficiently suppressed by the plurality of swirl breakers, so that the self-excited vibration of the rotor due to the swirl flow can be efficiently suppressed.

(14) In some embodiments, in the configuration of (12) or (13) above, the flow guide may have a radial inner surface that forms part of a fluid flow path in the rotating machine. Good.

(15) In some embodiments, in any of the configurations (12) to (14), the plurality of swirl breakers are radially outside the outer shroud and in the axial direction with the outer shroud. It has overlapping areas of overlap.

According to the configuration of (15) above, the projected area of the swirl breaker when viewed from the circumferential direction can be increased as compared with the case where the overlapping region is not provided, and the effect of suppressing the swirling flow component by the swirl breaker can be increased. Will increase.

(16) In some embodiments, in the configuration of (15), the gap between the plurality of swirl breakers and the outer peripheral surface of the outer shroud in the radial direction in the overlapping region has a diameter larger than that of the outer peripheral surface. It is larger than the gap between the seal fin provided on the outer side in the direction and extending in the circumferential direction and the outer peripheral surface.

According to the configuration of (16) above, it becomes difficult for the swirl breaker and the outer shroud to come into contact with each other.

(17) In some embodiments, in any of the configurations (12) to (16), the swirl breaker assembly is provided on the governor stage of the rotating machine.

According to the configuration of (17) above, the occurrence of self-excited vibration can be suppressed in the speed governor stage where self-excited vibration due to the swirl flow is likely to occur.

(18) The swirl breaker assembly according to at least one embodiment of the present invention is
An annular body connected to the radial inner end of the vane and extending along the circumferential direction,
A rotating member that can rotate in the circumferential direction with respect to the annular body,
A plurality of swirl breakers provided on the annular body at intervals in the circumferential direction,
A flow guide that projects axially from the rotating member so as to extend along the circumferential direction at a position displaced outward in the radial direction with respect to the plurality of swirl breakers.
To be equipped.

For example, in a rotating machine such as a steam turbine, the working fluid deviating from the main flow path is described above in the space between the annular body and the surface of the rotor shaft which is a rotating member that can rotate in the circumferential direction with respect to the annular body. It is conceivable that the turbine flows in while having a swirling flow component.
According to the configuration (18) above, the working fluid that is about to deviate from the main flow path is guided axially along the radial outer surface of the flow guide before flowing from the main flow path into the space. Therefore, the working fluid is less likely to deviate from the main flow path.
The working fluid deviating from the main flow path after being axially guided along the radial outer surface of the flow guide will be directed to the swirl breakers. That is, the working fluid deviated from the main flow path is guided by the swirl breaker. As a result, the swirling flow component of the working fluid deviated from the main flow path can be efficiently suppressed by the plurality of swirl breakers, so that the self-excited vibration of the rotor due to the swirl flow can be efficiently suppressed.

(19) The swirl breaker assembly according to at least one embodiment of the present invention is
A dummy ring that constitutes at least a part of the dummy seal portion in the turbine and extends along the circumferential direction,
A plurality of swirl breakers provided on the inner surface of the dummy ring at intervals in the circumferential direction and projecting in the axial direction,
To be equipped.

For example, in a rotating machine such as a steam turbine, the working fluid deviating from the main flow path creates a gap between the inner surface of the dummy ring and the surface of the rotor shaft facing the inner surface while maintaining the swirling flow component as described above. It is possible that it will flow.
According to the configuration of (19) above, it is prevented that the working fluid deviated from the main flow path flows in the circumferential direction by a plurality of swirl breakers provided on the inner surface of the dummy ring at intervals in the circumferential direction and protruding in the axial direction. Will be done. As a result, the swirling flow component of the working fluid deviated from the main flow path can be efficiently suppressed by the plurality of swirl breakers, so that the self-excited vibration of the rotor due to the swirl flow can be efficiently suppressed.

(20) In some embodiments, in the configuration of (19) above,
A rotor shaft that is arranged at a distance from the inner surface and that can rotate in the circumferential direction,
A flow guide protruding in the axial direction from the rotor shaft so as to extend along the circumferential direction at a position shifted inward in the radial direction with respect to the plurality of swirl breakers.
Further prepare.

According to the configuration of (20) above, when the working fluid deviating from the main flow path flows through the gap between the inner surface of the dummy ring and the surface of the rotor shaft, it is guided outward in the radial direction by the flow guide, and a plurality of working fluids are guided. We will head to the swirl breaker. As a result, the swirling flow component of the working fluid deviated from the main flow path can be efficiently suppressed by the plurality of swirl breakers, so that the self-excited vibration of the rotor due to the swirl flow can be efficiently suppressed.

(21) The rotary machine according to at least one embodiment of the present invention includes a swirl breaker assembly having any of the above configurations (18) to (20).

According to the configuration of the above (21), since the swirl breaker assembly having the configuration of any one of the above (18) to (20) is provided, the self-excited vibration of the rotor due to the swirl flow can be efficiently suppressed.

According to at least one embodiment of the present invention, the generation of self-excited vibration in a rotating machine can be suppressed.

FIG. 6 is a schematic cross-sectional view of a turbine comprising a swirl breaker assembly according to some embodiments. It is an enlarged perspective view about the part A in FIG. FIG. 3 is a view taken along the line III in FIG. It is a figure for demonstrating the swirl breaker assembly which concerns on one Embodiment. It is a figure for demonstrating the swirl breaker assembly which concerns on other embodiment. It is a figure for demonstrating the swirl breaker assembly which concerns on still another embodiment. It is a figure for demonstrating the swirl breaker assembly which concerns on still another embodiment. It is a figure for demonstrating the swirl breaker assembly which concerns on still another embodiment. It is a figure for demonstrating the swirl breaker assembly which concerns on still another embodiment. It is a figure which shows typically the moving blade in the stage on the upstream side in the axial direction, and the stationary blade in the stage on the downstream side in the axial direction, out of two stages adjacent to each other in the axial direction. It is sectional drawing which shows typically the structure of the turbine on the upstream side in the axial direction from the speed governor stage.

Hereinafter, some embodiments of the present invention will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, etc. of the components described as embodiments or shown in the drawings are not intended to limit the scope of the present invention to this, but are merely explanatory examples. Absent.
For example, expressions that represent relative or absolute arrangements such as "in a certain direction", "along a certain direction", "parallel", "orthogonal", "center", "concentric" or "coaxial" are exact. Not only does it represent such an arrangement, but it also represents a state of relative displacement with tolerances or angles and distances to the extent that the same function can be obtained.
For example, expressions such as "same", "equal", and "homogeneous" that indicate that things are in the same state not only represent exactly the same state, but also have tolerances or differences to the extent that the same function can be obtained. It shall also represent the state of existence.
For example, an expression representing a shape such as a quadrangular shape or a cylindrical shape not only represents a shape such as a quadrangular shape or a cylindrical shape in a geometrically strict sense, but also an uneven portion or chamfering within a range in which the same effect can be obtained. The shape including the part and the like shall also be represented.
On the other hand, the expressions "equipped", "equipped", "equipped", "included", or "have" one component are not exclusive expressions that exclude the existence of other components.

FIG. 1 is a schematic cross-sectional view of a turbine comprising a swirl breaker assembly according to some embodiments.
As shown in FIG. 1, the turbine 1 according to some embodiments is a so-called axial flow turbine, which includes a casing 2, a rotor shaft 4, a rotor disk 6 fixed to the rotor shaft 4, and a speed control stage. It includes a nozzle 8, a moving blade 12, and a stationary blade 14.
In the following description, the extending direction of the rotor shaft 4 is also simply referred to as an axial direction, and the circumferential direction of the rotor shaft 4 is also simply referred to as a circumferential direction. Further, regarding the axial direction, the direction along the axial direction of the main flow of the working fluid in the casing 2 is also referred to as a downstream direction or a downstream side, and a direction opposite to the downstream direction is also referred to as an upstream direction or an upstream side. In FIG. 1, the right side in the drawing is the downstream side, and the left side in the drawing is the upstream side.
Further, in the following description, the radial direction of the rotor shaft 4 is also simply referred to as a radial direction. Of the radial directions, the direction closer to the axis AX of the rotor shaft 4 is the radial inner side, and the direction away from the axis AX of the rotor shaft 4 is the radial outer direction.

A plurality of moving blades 12 are attached to the outer peripheral portion of the rotor disk 6 at intervals in the circumferential direction. The moving blade 12 has a moving blade main body 121 and an outer shroud 123 connected to each tip of the plurality of moving blade main bodies 121. The rotor blade stage 30 is formed by the rotor disk 6 and the plurality of moving blades 12 attached to the rotor disk 6.

A plurality of stationary blades 14 are arranged at intervals in the circumferential direction, and the inner end in the radial direction is attached to the outer peripheral surface of the inner peripheral ring 16, and the outer end in the radial direction is the inner circumference of the outer ring 18. It is attached to the surface. The stationary blade stage 40 is formed by a stationary blade ring 22 including an inner peripheral ring 16, an outer peripheral ring 18, and a plurality of stationary blades 14 attached to the respective rings 16 and 18.
In the turbine 1 according to some embodiments, the rotor blade stages 30 and the stationary blade stages 40 are alternately arranged along the axial direction. In FIG. 1, the moving blade stage 31 including the speed controlling stage moving blade 12A arranged on the immediately downstream side of the speed controlling stage nozzle 8 and the first stationary blade arranged on the immediately downstream side of the moving blade stage 31. The stage 41 and the first rotor blade stage 32 arranged immediately downstream of the first stationary blade stage 41 are shown.

In the turbine 1 according to some embodiments, one stage 7 is formed for each pair of the rotor blade stage 30 and the stationary blade stage 40 arranged adjacent to the rotor blade stage 30 on the upstream side in the axial direction. ing.
In the turbine 1 according to some embodiments, the most upstream stage 7 of the plurality of stages 7 forms the speed governor stage 7a. The speed governor stage 7a adjusts the rotation speed of the rotor shaft 4 by adjusting the flow rate of the working fluid sent to the stage 7 on the downstream side in the axial direction from the speed control stage 7a.

The speed governor nozzle 8 is supported by an inlet portion 54 fixed to the casing 2 and feeds in working fluid (steam, combustion gas).

In the turbine 1 according to some embodiments shown in FIG. 1, the working fluid flowing into the inlet portion 54 through the working fluid supply pipe 52 fixed to the casing 2 is the speed governing stage nozzle 8 and the speed controlling stage. It flows into the moving blade 12A and performs expansion work. The working fluid then flows into the stationary blade stage 40 and the moving blade stage 30 on the downstream side to perform expansion work. As a result, the rotor shaft 4 is rotationally driven.

In the turbine 1 according to some embodiments shown in FIG. 1, the working fluid deviated from the main flow path flows toward the downstream side from the gap between the outer peripheral surface 123a of the outer shroud 123 of the rotor blade 12 and the casing 2. A seal fin 81 is provided to suppress this. In the turbine 1 according to some embodiments shown in FIG. 1, as shown in FIGS. 4 to 9 described later, the radial outer base end portion 81a of the seal fin 81 is fixed to the casing 2 side, and the seal fin 81 is radially outer. The inner tip portion 81b faces the outer peripheral surface of the outer shroud 123 at a distance.
In some embodiments, the seal portion 80 that seals between the rotor blade 12 and the casing 2 includes a seal fin 81 and an outer shroud 123.

In some embodiments, the base end 81a of the seal fin 81 in the governor 7a is fixed at the inlet 54 to the inner peripheral surface 54a radially opposed to the outer shroud 123 of the governor blade 12A. However, it may be fixed to a member different from the inlet portion 54.
In some embodiments, the base end 81a of the seal fin 81 for the first rotor blade stage 32 is fixed to the outer peripheral surface 18a of the outer ring 18 which is radially opposed to the outer shroud 123 of the rotor blade 12. However, it may be fixed to a member different from the outer peripheral ring 18.
In some embodiments, at least one seal fin 81 is provided with respect to the outer shroud 123. In the embodiment exemplified in FIG. 1, two seal fins 81 are provided so as to be spaced apart from each other along the axial direction with respect to the outer shroud 123.

(About self-excited vibration in turbine 1)
As described above, in an axial-flow rotating machine such as the turbine 1, the working fluid deviating from the main flow path is discharged from the speed control stage nozzle 8 or the seal portion for sealing between the rotor shaft 4 or the moving blade 12 and the casing 2. It is known that a swirling flow (so-called swirl flow) is generated in the circumferential direction by flowing in with the swirling flow component given when passing through the stationary blade 14. When the rotor shaft 4 is eccentric due to the swirl flow, a sinusoidal pressure distribution having a peak in a direction different from the eccentric direction of the rotor shaft 4 is generated in the circumferential direction of the rotor shaft 4, for example, with high output operation. When the swirl flow increases, it may cause self-excited vibration of the rotor shaft 4. Therefore, various structures for suppressing the swirl flow in the seal portion have been devised.

However, in recent years, in axial-flow rotating machines such as steam turbines and gas turbines, the rotor diameter tends to be smaller and the blades tend to be multi-staged in order to improve turbine efficiency. Therefore, since the rotor shaft 4 has a smaller diameter and a longer shaft, self-excited vibration of the rotor shaft 4 tends to occur easily. Therefore, there is a need for a countermeasure plan for more effectively suppressing self-excited vibration.

Therefore, in some embodiments, the self-excited vibration of the rotor shaft 4 is suppressed by suppressing the swirl flow as follows. The details will be described below.
FIG. 2 is an enlarged perspective view of the inlet portion 54 side of the portion A surrounded by the broken line in FIG. 1, that is, the portion where the inlet portion 54 and the speed governor blade 12A face each other. In FIG. 2, the description of the speed governor blade 12A is omitted.
FIG. 3 is a view taken along the line III in FIG. 2, which is a view of the entrance portion 54 viewed from the downstream side in the axial direction.
FIG. 4 is a diagram for explaining a swirl breaker assembly according to an embodiment, and is a diagram for a part A surrounded by a broken line in FIG.
FIG. 5 is a diagram for explaining a swirl breaker assembly according to another embodiment, and is a diagram corresponding to FIG. 4.
FIG. 6 is a diagram for explaining a swirl breaker assembly according to still another embodiment, and is a diagram corresponding to FIG. 4.
FIG. 7 is a diagram for explaining a swirl breaker assembly according to still another embodiment, and is a diagram corresponding to FIG. 4.
FIG. 8 is a diagram for explaining a swirl breaker assembly according to still another embodiment, and is a diagram corresponding to FIG. 4.
FIG. 9 is a diagram for explaining a swirl breaker assembly according to still another embodiment, and is a diagram corresponding to FIG.

The entrance portion 54 is an annular member extending along the circumferential direction. In the following description, the portion of the inlet portion 54 including the region downstream of the speed governor nozzle 8 in the axial direction and radially outside the speed governor nozzle 8 is also referred to as an annular body 56.

As shown in FIGS. 2 to 9, in some embodiments, a flow guide 110 projecting from the annular body 56 to the downstream side in the axial direction is formed. In some embodiments, the flow guide 110 is axially upstream of the rotor blade body 121 and radially inward of the outer outer peripheral surface 123a of the outer shroud 123 toward the downstream side. It is protruding.

In some embodiments, the inlet 54 has an inner peripheral surface 54b that forms a fluid flow path 65 through which the working fluid flows. The inner peripheral surface 54b forms a fluid flow path 65 on the radial outer side of the speed governor nozzle 8.
In some embodiments, the region downstream of the inner peripheral surface 54b is the radial inner inner peripheral surface 111 of the flow guide 110. That is, as shown in FIGS. 2 to 9, in some embodiments, the inner peripheral surface 111 of the flow guide 110 facing inward in the radial direction forms a part of the fluid flow path 65 in the turbine 1.

As shown in FIGS. 2 to 9, in some embodiments, the flow guide 110 has a guide surface 115 that points to a plurality of swirl breaker sides described later in the radial direction. In the embodiments shown in FIGS. 2 to 9, the guide surface 115 points outward in the radial direction. In the embodiment shown in FIGS. 2 to 9, the guide surface 115 has a conical surface that is inclined outward in the radial direction toward the upstream side in the axial direction, but in the region on the upstream side in the axial direction and the region on the downstream side. It may have cylindrical surfaces of equal diameter, or it may have a conical surface that is inclined inward in the radial direction toward the upstream side in the axial direction. The flow guide 110 may be formed over the entire circumference in the circumferential direction, or may have a region that is not formed in a part of the circumferential direction.

As shown in FIGS. 2 to 9, in some embodiments, the annular body 56 connects the annular body side facing wall surface 57 facing the guide surface 115 in the radial direction, and the guide surface 115 and the annular body side facing wall surface 57. It has an annular body side wall surface 58.
As shown in FIGS. 2 to 9, in some embodiments, the annular body-side facing wall surface 57 is an inner peripheral surface 54a that is radially opposed to the outer shroud 123 of the speed governor blade 12A at the inlet portion 54. is there.
As shown in FIGS. 2 to 9, in some embodiments, the annular side wall surface 58 is a surface extending radially and circumferentially between the guide surface 115 and the annular body side facing wall surface 57, but has a diameter. It may be inclined with respect to the radial direction so as to move toward the upstream side or the downstream side in the axial direction toward the outside in the direction. The annular side wall surface 58 is located axially upstream of the axially protruding end 113 of the flow guide 110.

As shown in FIGS. 2 to 9, in some embodiments, a space is formed between the guide surface 115, the annular side wall surface 58, and the annular body side facing wall surface 57, and this space is referred to as a cavity 67.

As shown in FIGS. 2 to 9, in some embodiments, a plurality of swirl breakers 130 are provided on the annular body 56 at positions displaced in the radial direction with respect to the flow guide 110 at intervals in the circumferential direction. More specifically, each of the plurality of swirl breakers 130 projects radially outward from the flow guide 110 on the downstream side in the axial direction. As shown in FIGS. 2-9, in some embodiments, each of the plurality of swirl breakers 130 has a cavity 67, at least in part thereof, between the guide surface 115, the annular side wall surface 58, and the annular side facing wall surface 57. Exists in.

As shown in FIGS. 2-9, in some embodiments, each of the plurality of swirl breakers 130 has a plate shape extending along the axial and radial directions.
As a result, the shape of the swirl breaker 130 becomes a simple shape, so that it is easy to form. The shape of the swirl breaker 130 is not limited to the plate shape as described above, and may be columnar.

The annular body 56 including the above-mentioned flow guide 110 and the plurality of swirl breakers 130 is also referred to as a swirl breaker assembly 100.

As shown in FIG. 1, in some embodiments, the swirl breaker assembly 100 is provided in the governor 7a and the governor 7 downstream of the governor 7a. The swirl breaker assembly 100 may be provided at least in any one of the stages 7.
In the swirl breaker assembly 100B provided in the stage 7 on the downstream side of the speed governor stage 7a, a flow guide 110 and a plurality of swirl breakers 130 are provided in the outer peripheral ring 18 instead of the inlet portion 54. ..

In the following description, the swirl breaker assembly 100A provided on the governor stage 7a and the swirl breaker assembly 100B provided on the stage 7 downstream of the speed governor 7a have the same basic configuration. Therefore, the swirl breaker assembly 100A provided in the speed governor stage 7a will be described in detail, and the description of the swirl breaker assembly 100B provided in the stage 7 downstream of the speed governor stage 7a will be omitted. In the following description, it is not necessary to distinguish between the swirl breaker assembly 100A provided on the speed governor stage 7a and the swirl breaker assembly 100B provided on the stage 7 downstream of the speed governor stage 7a. In this case, the description of the alphabet after the number of the code is simply omitted, and it is simply referred to as the swirl breaker assembly 100.

In some embodiments shown in FIGS. 2-9, as indicated by arrow a in FIG. 4, the working fluid deviating from the main flow path, i.e. the fluid flow path 65, is the outer shroud 123 that includes the cavity 67 from the fluid flow path 65. When flowing into the space between the inner peripheral surface of the casing 2 and the inner peripheral surface of the casing 2, the fluid guide 110 is guided along the guide surface 115 which is the outer surface in the radial direction as shown by the arrow b in FIG. The working fluid guided along the guide surface 115 is guided toward the plurality of swirl breakers 130 as shown by the arrow c in FIG. That is, in some embodiments shown in FIGS. 2 to 9, the working fluid deviated from the fluid flow path 65 can be efficiently guided to the swirl breaker 130.

In some embodiments shown in FIGS. 2 to 9, since the working fluid flowing into the cavity 67 has a swirling flow component flowing in the circumferential direction, the working fluid flows outward in the radial direction in the cavity 67 along the circumferential direction. It flows. In some embodiments shown in FIGS. 2-9, each of the plurality of swirl breakers 130 projects axially within the cabidi 67 to prevent the working fluid from flowing circumferentially.
In some embodiments shown in FIGS. 2 to 9, as described above, the working fluid deviated from the fluid flow path 65 can be efficiently guided to the swirl breaker 130, so that the working fluid deviated from the fluid flow path 65 has. The swirl flow component can be efficiently suppressed by a plurality of swirl breakers 130. As a result, the self-excited vibration of the rotor shaft 4 due to the swirl flow can be efficiently suppressed.

As described above, in some embodiments shown in FIGS. 2-9, since the flow guide 110 has a guide surface 115, the working fluid deviating from the main flow path is efficiently guided to the swirl breaker 130 by the guide surface 115. The fluid.

Hereinafter, the swirl breaker 130 according to some embodiments will be further described with reference to the respective drawings of FIGS. 2 to 9.
In some embodiments shown in FIGS. 2-4, 6, 7, and 9, the radially inner end 131 of the swirl breaker 130 is separated from the guide surface 115 of the flow guide 110.
On the other hand, in the swirl breaker 130 according to the embodiment shown in FIGS. 5 and 8, the radial inner end 131 is connected to the guide surface 115 of the flow guide 110.

When the end 131 of the plurality of swirl breakers 130 is not connected to the flow guide 110, a part of the working fluid deviated from the main flow path is in the circumferential direction from between the end 131 and the guide surface 115 of the flow guide 110. Will flow to.
On the other hand, in the swirl breaker 130 according to the embodiment shown in FIGS. 5 and 8, since the radial inner end 131 is connected to the guide surface 115 of the flow guide 110 as described above, the end 131 It is possible to suppress a part of the working fluid from flowing in the circumferential direction between the flow guide 110 and the guide surface 115 of the flow guide 110, and the effect of suppressing the swirling flow component by the swirl breaker 130 is enhanced. Further, in the swirl breaker 130 according to the embodiment shown in FIGS. 5 and 8, the projected area of the swirl breaker 130 when viewed from the circumferential direction can be increased, and the effect of suppressing the swirling flow component by the swirl breaker 130 is enhanced.

In the swirl breaker 130 according to some embodiments shown in FIGS. 2 to 9, the radial outer end 132 is connected to the annular body side facing wall surface 57. In some embodiments shown in FIGS. 2 to 9, the swirl breaker 130 may have a radial outer end 132 separated from the annular body side facing wall surface 57.

The swirl breaker 130 according to some embodiments shown in FIGS. 2 to 9 overlaps the flow guide 110 at least partially in the axial direction.
In this way, since the swirl breaker 130 overlaps with the flow guide 110 in the axial direction, the working fluid deviated from the main flow path is efficiently guided to the swirl breaker 130 by the flow guide 110.

In the embodiment shown in FIGS. 5 and 7, the tip portion 133 along the axial direction of the swirl breaker 130 is located axially upstream of the axially protruding end 113 of the flow guide 110.
On the other hand, in some embodiments shown in FIGS. 2 to 4, 6, 8 and 9, the tip 133 of the swirl breaker 130 is axially downstream of the protruding end 113 of the flow guide 110. positioned. That is, in some embodiments shown in FIGS. 2-4, 6, 8, and 9, the flow guide 110 swirls the axial position of the axially protruding end 113 with respect to the axial direction. It exists between the base end 134 and the tip 133 of the breaker 130.
As described above, when the axial position of the flow guide 110 with respect to the protruding end 113 exists between the base end portion 134 and the tip end portion 133 of the swirl breaker 130, the swirl breaker 130 is radially outside the protruding end 113. There will be a region between the base end 134 and the tip 133. Therefore, when the working fluid deviating from the main flow path flows radially outward from the protruding end 113 of the flow guide 110 while flowing in the circumferential direction, the side surface of the swirl breaker 130, that is, the base end portion 134 and the tip end portion 133 of the swirl breaker 130. You will reach the area between. Therefore, according to some embodiments shown in FIGS. 2-4, 6, 8, and 9, the working fluid deviating from the main flow path is efficiently guided to the swirl breaker 130 by the flow guide 110.
As in the embodiment shown in FIG. 8, the position of the tip portion 133 in the axial direction may differ depending on the position in the radial direction.

As described above, in some embodiments shown in FIGS. 2-9, since the plurality of swirl breakers 130 are present in the cavity 67, the working fluid guided to the cavity 67 is the plurality of swirl breakers present in the cavity 67. The swirling flow component is suppressed by 130. As a result, the effect of suppressing the swirling flow component by the swirl breaker 130 is enhanced.

In some embodiments shown in FIGS. 2-5 and 7-9, the tip 133 of the swirl breaker 130 is separated from the seal fin 81.
On the other hand, in the embodiment shown in FIG. 6, the swirl breaker 130 is connected to a seal fin 81 having a tip portion 133 extending in the circumferential direction.
When the tip 133 of the swirl breaker 130 is not connected to the seal fin 81, as in some embodiments shown in FIGS. 2-5 and 7-9, for some of the working fluid deviated from the main flow path. Since the fluid flows in the circumferential direction from between the tip portion 133 and the seal fin 81, the effect of suppressing the swirling flow component by the swirl breaker 130 is reduced as compared with the case where the tip portion 133 and the seal fin 81 are connected. It ends up.
On the other hand, according to the embodiment shown in FIG. 6, the effect of suppressing the swirling flow component by the swirl breaker 130 is enhanced. Further, according to the embodiment shown in FIG. 6, the projected area of the swirl breaker 130 when viewed from the circumferential direction can be increased, and the effect of suppressing the swirling flow component by the swirl breaker 130 is enhanced.

In some embodiments shown in FIGS. 2-9, for example, as shown in FIGS. 4 and 9, the swirl breaker 130 has a hem spread in which the circumferential dimension gradually increases toward the proximal end 134 in the axial direction. Has a shape. That is, in some embodiments shown in FIGS. 2 to 9, for example, as shown in FIGS. 4 and 9, the base end 134 of the swirl breaker 130 has a curved surface that is gently connected to the annular side wall surface 58. The connecting portion 134a is formed.
As a result, the circumferential dimension of the swirl breaker 130 on the proximal end 134 side is increased, so that the bending strength of the swirl breaker 130 in the circumferential direction is improved. Further, since the shape of the swirl breaker 130 on the base end 134 side is a hem-spreading shape, it becomes easy to form the swirl breaker 130 when the swirl breaker 130 is formed by, for example, cutting out in the annular body 56.
In the swirl breaker 130 according to some embodiments, the connection portion between the radial outer end portion 132 and the annular body side facing wall surface 57 and the connection portion between the radial inner end portion 131 and the guide surface 115 are described above. It may be formed in the same manner as the connection portion 134a.

In the embodiments shown in FIGS. 5 and 7, the swirl breaker 130 does not overlap the outer shroud 123 in the axial direction.
On the other hand, in the embodiment shown in FIGS. 4, 6, 8 and 9, the swirl breaker 130 has an overlapping region 137 axially overlapping with the outer shroud 123 on the radial outer side of the outer shroud 123. Have.
As a result, the projected area of the swirl breaker 130 when viewed from the circumferential direction can be increased as compared with the case where the overlapping region 137 is not provided as in the embodiment shown in FIGS. 5 and 7, and the swirl breaker 130 can be increased. The effect of suppressing the swirling flow component is enhanced.

In the embodiment shown in FIGS. 4, 6, 8 and 9, the gap 69a between the swirl breaker 130 and the radial outer outer peripheral surface 123a of the outer shroud 123 in the overlapping region 137 is formed between the seal fin 81 and the outer peripheral surface 123a. It is larger than the gap 69b with.
This makes it difficult for the swirl breaker 130 and the outer shroud 123 to come into contact with each other.

In the embodiment shown in FIG. 9, the swirl breaker 130 is thinner in the circumferential direction on the flow guide 110 side when viewed in the radial direction in the region on the tip side in the axial direction. That is, the swirl breaker 130 according to the embodiment shown in FIG. 9 is a thin portion which is a region on the downstream side in the axial direction and is thinner in the circumferential direction than the other regions in the vicinity of the end portion 131 on the inner side in the radial direction. It has 139.
Of the parts of the swirl breaker 130, the part on the flow guide 110 side when viewed in the radial direction in the region on the tip side in the axial direction is located near the outer shroud 123, which is the radial outer end of the rotor blade 12. Be placed. Therefore, there is a possibility that the portion and the outer shroud 123 come into contact with each other due to heat expansion or the like due to the operation of the turbine 1.
In that respect, in the swirl breaker 130 according to the embodiment shown in FIG. 9, a thin-walled portion 139 is provided at the portion. As a result, compared to the case where the thickness of the portion in the circumferential direction is the same as that of other portions, even if the portion comes into contact with the outer shroud 123, the influence on the moving blade 12 is suppressed. it can.
The thin portion 139 may be formed so as to include the overlapping region 137 along the axial direction.

In some embodiments shown in FIGS. 2-9, the plurality of swirl breakers 130 may be provided at equal intervals in the circumferential direction.
When the amount of the working fluid sent into the turbine 1 fluctuates, the flow of the working fluid deviating from the main flow path also changes. Therefore, a plurality of swirl breakers 130 provided in the annular body 56 are unevenly arranged along the circumferential direction. It is desirable to arrange them evenly in terms of suppressing swirl flow. Therefore, according to some embodiments shown in FIGS. 2 to 9, the arrangement positions of the plurality of swirl breakers 130 along the circumferential direction are appropriate.

The swirl breaker assembly 100 of any of the several embodiments shown in FIGS. 2 to 9 may be provided in the governor stage 7a.
As a result, the occurrence of self-excited vibration can be suppressed in the speed governor stage 7a where self-excited vibration due to the swirl flow is likely to occur.

Note that the swirl breaker assembly 100 of any of the several embodiments shown in FIGS. 2 to 9 may be attached to the existing turbine 1 when the existing turbine 1 is repaired. In this case, the swirl breaker assembly 100 of any of the several embodiments shown in FIGS. 2 to 9 may be arranged on the upstream side of the moving blade 12 of the existing turbine 1 as follows. That is, the swirl breaker assembly 100 of any of the several embodiments shown in FIGS. 2 to 9 is placed on the downstream side in the axial direction, for example, when the flow guide 110 is radially inside the outer peripheral surface 123a of the outer shroud 123. It is preferable to arrange it so that it protrudes toward it. Further, the swirl breaker assembly 100 of any of the several embodiments shown in FIGS. 2 to 9 is provided so that, for example, a plurality of swirl breakers 130 project radially outward from the flow guide 110 to the downstream side in the axial direction. It is good to place it in.

The present invention is not limited to the above-described embodiment, and includes a modified form of the above-described embodiment and a combination of these embodiments as appropriate.
For example, in some of the above-described embodiments, the above-mentioned swirl breaker assembly 100 is applied to a sealing portion 80 that seals between the rotor blade 12 and the casing 2. However, the swirl breaker assembly 100 described above may be applied to the seal portion that seals between the rotor shaft 4 and the casing 2 (between the rotor shaft 4 and the stationary blade 14). For example, among the inlet portions 54, the above-mentioned flow guide 110 and a plurality of flow guides 110 are formed on the axially downstream side surface 54c (see FIG. A swirl breaker 130 may be provided. Further, for example, in the inner peripheral ring 16 connected to the radial inner end of the stationary blade 14, the above-mentioned flow guide 110 and a plurality of swirl breakers 130 are provided on the surface 16c (see FIG. 1) on the downstream side in the axial direction. You may.

FIG. 10 is a diagram schematically showing a moving blade 12 in the step 7 on the upstream side in the axial direction and a stationary blade 14 in the step 7 on the downstream side in the axial direction among the two steps 7 adjacent to each other in the axial direction. is there.
For example, as shown in FIG. 10, a flow guide 110A and a swirl breaker 130A are provided in order to suppress a swirl flow flowing through a gap between the inner peripheral ring 16 and the surface 4a of the rotor shaft 4 in the stationary blade stage 40. You may.

As shown in FIG. 10, in the turbine 1 according to some embodiments, the working fluid deviating from the main flow path is the inner peripheral surface 16a on the radial inner side of the inner peripheral ring 16 in the stationary blade stage 40 and the inner peripheral surface thereof. A seal fin 83 is provided to prevent the flow from the gap between the surface 4a of the rotor shaft 4 facing the 16a toward the downstream side. In the turbine 1 according to some embodiments shown in FIG. 10, in the seal fin 83, the radial outer base end portion 83a is fixed to the inner peripheral surface 16a of the inner peripheral ring 16, and the radial inner tip portion 83b Is opposed to the surface 4a of the rotor shaft 4 at a distance.

In the embodiment shown in FIG. 10, the flow guide 110A is formed so as to project toward the downstream side in the axial direction on the surface 6a on the downstream side of the rotor disk 6. In the embodiment shown in FIG. 10, the flow guide 110A may be formed over the entire circumference in the circumferential direction, or may have a region that is not formed in a part of the circumferential direction. Further, in the embodiment shown in FIG. 10, the flow guide 110A may be formed on a platform (not shown) to which the base end portion of the airfoil portion of the moving blade 12 is connected.

In the embodiment shown in FIG. 10, a plurality of swirl breakers 130A are provided on the axially upstream side surface 16b of the inner peripheral ring 16 at positions deviated in the radial direction with respect to the flow guide 110A at intervals in the circumferential direction. .. More specifically, each of the plurality of swirl breakers 130A projects radially inward and upstream side in the axial direction with respect to the flow guide 110A.

That is, in the embodiment shown in FIG. 10, the swirl breaker assembly 100 includes an inner peripheral ring 16 which is an annular body connected to the radial inner end of the stationary blade 14 and extending along the circumferential direction. .. In the embodiment shown in FIG. 10, the swirl breaker assembly 100 includes a rotor shaft 4 which is a rotating member that can rotate in the circumferential direction with respect to the inner peripheral ring 16. In the embodiment shown in FIG. 10, the swirl breaker assembly 100 includes a plurality of swirl breakers 130A provided on the inner peripheral ring 16 at intervals in the circumferential direction. In the embodiment shown in FIG. 10, the swirl breaker assembly 100 extends axially from the rotor shaft 4 at positions offset radially outward with respect to the plurality of swirl breakers 130A so as to extend along the circumferential direction. A protruding flow guide 110A is provided.

In the embodiment shown in FIG. 10, the working fluid that tends to deviate from the main flow path, that is, the fluid flow path 65 is the inner peripheral surface 16a on the inner peripheral surface of the inner peripheral ring 16 in the radial direction from the fluid flow path 65 and the surface 4a of the rotor shaft 4. Before flowing into the gap between the fluids, the fluid guide 110A is guided to the downstream side in the axial direction along the guide surface 115A, which is the outer surface in the radial direction, as shown by the arrow d in FIG. Therefore, the working fluid is guided toward the stationary blade 14 in the step 7 on the downstream side in the axial direction, so that it is difficult to deviate from the fluid flow path 65.
The working fluid that has been guided downstream along the guide surface 115A and then deviated from the fluid flow path 65 is directed to the plurality of swirl breakers 130A as shown by the arrow e. That is, in the embodiment shown in FIG. 10, the working fluid deviating from the fluid flow path 65 is guided by the swirl breaker 130A.

In the embodiment shown in FIG. 10, the working fluid guided by the swirl breaker 130A is prevented from flowing in the circumferential direction by each of the plurality of swirl breakers 130A even if it has a swirling flow component flowing in the circumferential direction. ..

FIG. 11 is a cross-sectional view schematically showing the structure of the turbine 1 on the upstream side in the axial direction from the speed governor stage 7a. In the turbine 1 according to some embodiments, a dummy seal portion 70 is provided on the upstream side in the axial direction from the speed governor stage 7a. The dummy seal portion 70 includes a dummy ring 71 and seal fins 85 and 87. In the following description, the left direction in the drawing, which has been referred to as the upstream side in the axial direction, is also referred to as the dummy seal side, and the right direction in the drawing, which has been referred to as the downstream side in the axial direction, is also referred to as the passenger compartment side.

As shown in FIG. 11, in the turbine 1 according to some embodiments, the seal fins 85 and 87 are working fluids deviated from the fluid flow path 65 between the speed control stage nozzle 8 and the speed control stage rotor blade 12A. Is provided to prevent the flow from the inner surface 71a on the inner side of the dummy ring 71 in the radial direction and the surface 4a of the rotor shaft 4 facing the inner surface 71a toward the dummy seal side. In the turbine 1 according to some embodiments shown in FIG. 11, the seal fins 85, 87 have radial outer base end portions 85a, 87a fixed to the inner surface 71a of the dummy ring 71, and the radial inner tip portion. 85b and 87b face the surface 4a of the rotor shaft 4 at intervals.
In the embodiment shown in FIG. 11, the diameter of the rotor shaft 4 is larger in the second region 402 facing the inner surface 71a of the dummy ring 71 than in the first region 401 in which the above-mentioned stages 7 are arranged. Further, in the embodiment shown in FIG. 11, the diameter of the rotor shaft 4 is configured to be larger than the second region 402 in the dummy seal side of the second region 402, that is, in the third region 403 on the left side of the drawing. You may be. In the embodiment shown in FIG. 11, the seal fin 85 faces the surface 4a in the second region 402 of the rotor shaft 4, and the seal fin 87 faces the surface 4a in the third region 403 of the rotor shaft 4. ..

In the embodiment shown in FIG. 11, a plurality of swirl breakers 130B are spaced apart from the inner surface 71a of the dummy ring 71 in the circumferential direction on the vehicle interior side of the seal fin 85 arranged to face the surface 4a in the second region 402. May be placed with a space.
Further, in the embodiment shown in FIG. 11, a plurality of swirl breakers 130C are provided on the inner surface 71a of the dummy ring 71 in the circumferential direction on the vehicle interior side of the seal fin 87 arranged to face the surface 4a in the third region 403. It may be arranged at intervals.

In the embodiment shown in FIG. 11, in the rotor shaft 4, the flow guide 110B may be provided so as to project toward the vehicle interior side in a region where the diameter gradually increases from the first region 401 to the second region 402. In the embodiment shown in FIG. 11, the flow guide 110B may be formed over the entire circumference in the circumferential direction, or may have a region that is not formed in a part of the circumferential direction. The flow guide 110B is an annular member provided separately from the rotor shaft 4 and may be attached to the rotor shaft 4, so that the rotor shaft 4 itself has the shape of the flow guide 110B as shown in FIG. The rotor shaft 4 may be formed on the surface.

That is, in the embodiment shown in FIG. 11, the swirl breaker assembly 100 constitutes at least a part of the dummy seal portion 70 in the turbine 1, and is spaced apart from the dummy ring 71 extending in the circumferential direction in the circumferential direction. A plurality of swirl breakers 130B and 130C which are provided on the inner surface 71a of the dummy ring 71 and project in the axial direction are provided.
Further, in the embodiment shown in FIG. 11, the swirl breaker assembly 100 is arranged at a distance from the inner surface 71a, and is radially inside with respect to the rotor shaft 4 that is rotatable in the circumferential direction and the plurality of swirl breakers 130B. A flow guide 110B that protrudes in the axial direction from the rotor shaft 4 is provided so as to extend along the circumferential direction at a position shifted to.

In the embodiment shown in FIG. 11, the working fluid that is about to deviate from the main flow path, that is, the fluid flow path 65 is the inner surface 71a on the radial inner side of the dummy ring 71 from the fluid flow path 65 and the rotor shaft 4 facing the inner surface 71a. It flows through the gap between the surface 4a and is guided outward in the radial direction by the flow guide 110B as shown by the arrow f in FIG. 11 toward the plurality of swirl breakers 130B. That is, in the embodiment shown in FIG. 11, the working fluid deviated from the fluid flow path 65 is guided to the swirl breaker 130B by the flow guide 110B.

In the embodiment shown in FIG. 11, the working fluid guided by the swirl breaker 130B is prevented from flowing in the circumferential direction by each of the plurality of swirl breakers 130B even if it has a swirling flow component flowing in the circumferential direction. ..

In the embodiment shown in FIG. 11, the working fluid that has passed between the surface 4a in the second region 402 and the seal fin 85 flows toward the seal fin 87 arranged to face the surface 4a in the third region 403. .. At that time, the working fluid is in the radial direction as shown by the arrow g due to the presence of the step portion 405 generated by the difference in diameter between the second region 402 and the third region 403, for example, as shown in FIG. It will be guided to the outside and head toward a plurality of swirl breakers 130C. That is, in the embodiment shown in FIG. 11, the working fluid deviated from the fluid flow path 65 is guided to the swirl breaker 130C by the step portion 405.

In the embodiment shown in FIG. 11, the working fluid guided by the swirl breaker 130C is prevented from flowing in the circumferential direction by each of the plurality of swirl breakers 130C even if it has a swirling flow component flowing in the circumferential direction. ..
In the embodiment shown in FIG. 11, when the rotor shaft 4 is formed so that the diameter of the rotor shaft 4 gradually increases from the second region 402 to the third region 403, the flow guide 110B described above is used. Similarly, a flow guide (not shown) may be provided so as to project toward the vehicle interior side in a region where the diameter gradually increases from the second region 402 to the third region 403.

1 Turbine 2 Casing 4 Rotor shaft 6 Rotor disk 7 Stage 7a Speed control stage 8 Speed control stage Nozzle 12 Moving blade 12A Speed control stage Moving blade 54 Inlet portion 56 Ring body 57 Ring body side facing wall surface 58 Ring body side wall surface 65 Fluid flow path 81 Seal fin 100 Swirl breaker assembly 110 Flow guide 113 Protruding end 115 Guide surface 121 Blade body 123 Outer shroud 130 Swirl breaker 137 Overlapping area 139 Thin wall

Claims (21)

1. An annular body that extends along the circumferential direction,
   A flow guide that projects axially from the annular body so as to extend along the circumferential direction.
   A plurality of swirl breakers provided on the annular body at positions displaced in the radial direction with respect to the flow guide at intervals in the circumferential direction.
   Swirl breaker assembly with.
2. The swirl breaker assembly according to claim 1, wherein the plurality of swirl breakers have their radial ends connected to the flow guide.
3. The swirl breaker assembly according to claim 1 or 2, wherein the plurality of swirl breakers overlap the flow guide at least partially in the axial direction.
4. The flow guide according to claims 1 to 3, wherein the axial position of the protruding end in the axial direction exists between the base end portion and the tip end portion of the plurality of swirl breakers along the axial direction. The swirl breaker assembly according to any one item.
5. The swirl breaker assembly according to any one of claims 1 to 4, wherein the flow guide has a guide surface that points to the plurality of swirl breaker sides in the radial direction.
6. The annular body has an annular body-side facing wall surface that faces the guide surface in the radial direction, and an annular body side wall surface that connects the guide surface and the annular body-side facing wall surface.
   The swirl breaker assembly according to claim 5, wherein the plurality of swirl breakers exist in a space between the guide surface, the annular side wall surface, and the annular body side facing wall surface.
7. The swirl breaker assembly according to any one of claims 1 to 6, wherein the plurality of swirl breakers are connected to a seal fin whose tip portion along the axial direction extends in the circumferential direction.
8. The swirl breaker assembly according to any one of claims 1 to 7, wherein the plurality of swirl breakers have a plate shape extending along the axial direction and the radial direction.
9. The swirl breaker assembly according to any one of claims 1 to 8, wherein the plurality of swirl breakers have a shape in which the dimension in the circumferential direction gradually increases toward the base end portion in the axial direction.
10. The plurality of swirl breakers according to any one of claims 1 to 9, wherein the flow guide side is thinner in the circumferential direction when viewed in the radial direction in the region on the tip side in the axial direction. The swirl breaker assembly described.
11. The swirl breaker assembly according to any one of claims 1 to 10, wherein the plurality of swirl breakers are provided at equal intervals in the circumferential direction.
12. The swirl breaker assembly according to any one of claims 1 to 11.
    A rotor disc that rotates around the axis in the casing,
    A plurality of rotor blade bodies attached to the rotor disk,
    An outer shroud connected to the tip of each of the plurality of rotor blade bodies,
    A rotating machine equipped with.
13. The flow guide protrudes toward the downstream side in the axial direction on the upstream side in the axial direction from the rotor blade body and on the inner side in the radial direction from the outer peripheral surface on the radial outer side of the outer shroud.
    The rotary machine according to claim 12, wherein the plurality of swirl breakers project outward in the radial direction from the flow guide to the downstream side in the axial direction.
14. The rotary machine according to claim 12 or 13, wherein the flow guide has an inner surface in the radial direction forming a part of a fluid flow path in the rotary machine.
15. The rotating machine according to any one of claims 12 to 14, wherein the plurality of swirl breakers have an overlapping region that overlaps the outer shroud in the axial direction on the radial outer side of the outer shroud.
16. In the overlapping region, the gap between the plurality of swirl breakers and the outer peripheral surface of the outer shroud on the radial outer side is provided on the radial outer side of the outer peripheral surface and extends in the circumferential direction. The rotating machine according to claim 15, which is larger than the gap with the outer peripheral surface.
17. The rotary machine according to any one of claims 12 to 16, wherein the swirl breaker assembly is provided in a speed governor stage of the rotary machine.
18. An annular body connected to the radial inner end of the vane and extending along the circumferential direction,
    A rotating member that can rotate in the circumferential direction with respect to the annular body,
    A plurality of swirl breakers provided on the annular body at intervals in the circumferential direction,
    A flow guide that projects axially from the rotating member so as to extend along the circumferential direction at a position displaced outward in the radial direction with respect to the plurality of swirl breakers.
    Swirl breaker assembly with.
19. A dummy ring that constitutes at least a part of the dummy seal portion in the turbine and extends along the circumferential direction,
    A plurality of swirl breakers provided on the inner surface of the dummy ring at intervals in the circumferential direction and projecting in the axial direction,
    Swirl breaker assembly with.
20. A rotor shaft that is arranged at a distance from the inner surface and that can rotate in the circumferential direction,
    A flow guide protruding in the axial direction from the rotor shaft so as to extend along the circumferential direction at a position shifted inward in the radial direction with respect to the plurality of swirl breakers.
    19. The swirl breaker assembly according to claim 19.
21. A rotary machine comprising the swirl breaker assembly according to any one of claims 18 to 20.

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