JP2017155859A - Seal device and rotary machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a seal device having a sufficient seal performance and capable of reducing swirl and a rotary machine.SOLUTION: A seal device 4 seals against a flow of fluid flowing between an outer peripheral surface of a rotor 2 that can be rotated around an axis line Ac and a casing 3 covering the rotor 2 from the outer peripheral side from one side in a direction of the axis line Ac to the other side. The seal device 4 comprises several seal fins 11 arranged at the inner peripheral surface of the casing 3 in a direction of the axis line Ac and several swirl breakers 12 connecting a first seal fin 11A positioned most nearly at one side of the axis line Ac direction of the several seal fins 11 with a second seal fin 11B arranged adjacent to the other side of the axis line Ac direction and arranged to be spaced apart in a peripheral direction, and the first seal fin 11A is formed with a penetration part 13 penetrating through the first seal fin 11A in a direction of an axis line Ac.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a sealing device and a rotary machine.

  For example, a rotary machine such as a steam turbine includes a rotor that extends along an axis, and a casing that covers the rotor from the outer peripheral side. On the outer peripheral surface of the rotor, moving blades arranged in the circumferential direction of the axis are provided in a plurality of stages. A plurality of stages of stationary blades are provided on the inner peripheral surface of the casing so as to be staggered in the axial direction with respect to the moving blade. When high-temperature and high-pressure steam flows between the rotor blades and the stationary blades, the rotor obtains rotational energy and is driven to rotate around the axis. The rotational motion of the rotor is used to drive a generator or the like connected to the shaft end.

  Here, in order to realize smooth rotation of the rotor, a certain clearance is generally provided between the outer peripheral end portion (shroud) of the moving blade as described above and the inner peripheral surface of the casing. However, since the steam flowing through the clearance flows away downstream without colliding with the moving blade, there is no contribution to the rotational drive of the rotor. Therefore, a technique for reducing the flow (leakage) of steam in this clearance as much as possible is required. As an example of such a technique, a technique described in Patent Document 1 below is known. The apparatus described in Patent Document 1 includes a plurality of labyrinth fins provided at intervals on an inner peripheral surface of a casing (stationary portion) that covers a rotating body.

  Furthermore, in the area | region between a pair of adjacent labyrinth fins, a swirl | vortex (swirl) is formed because a vapor | steam turns in the rotation direction of the said rotary body with rotation of a rotary body. When such a swirl develops, it is known that a whirling vibration (self-excited vibration) of the rotor (rotating body) occurs. Therefore, in the apparatus according to Patent Document 1 below, guide vanes are provided between the labyrinth fins.

JP 2007-120476 A

  However, in the technique described in Patent Document 1, since the guide vane has a great resistance to the flow of steam, the steam avoids the guide vane and flows into the gap between the labyrinth fin and the rotor. there is a possibility. In other words, the purpose of sealing the steam flow cannot be sufficiently achieved.

  The present invention has been made to solve the above problems, and an object of the present invention is to provide a sealing device and a rotary machine that have sufficient sealing performance and can reduce swirl.

  According to the first aspect of the present invention, the sealing device is provided from the one axial side to the other side between the outer peripheral surface of the rotating body that can rotate around the axis and the casing that covers the rotating body from the outer peripheral side. And a plurality of seal fins extending inward in the radial direction of the axial line from the inner peripheral surface of the casing and arranged in the axial direction, and the plurality of seal fins The first seal fin located on the one side in the axial direction and the second seal fin provided adjacent to the other side in the axial direction of the first seal fin are connected in the axial direction and in the circumferential direction. A plurality of swirl breakers arranged at intervals, and the first seal fin is formed with a penetrating portion penetrating the first seal fin in the axial direction.

  According to this configuration, since the through portion is formed in the first seal fin, the steam can be smoothly guided to the space between the first seal fin and the second seal fin through the through portion. The steam guided into the space forms a swirl flow that swirls in the circumferential direction of the axis, and the development of the swirl flow can be suppressed by the swirl breaker. That is, since the steam is actively guided toward the swirl breaker by providing the through portion, the swirl breaker can sufficiently function.

  According to the second aspect of the present invention, in the sealing device, the penetrating portion is a unit area defined by a pair of swirl breakers adjacent in the circumferential direction on the first seal fin. You may form in the area | region of the rotation direction front side of the said rotary body.

  The swirl flow is generated as the rotating body rotates. That is, this swirl flow flows from the rear side in the rotational direction of the rotating body toward the front side as it goes from one side in the axial direction to the other side. According to the above configuration, since the through portion is formed in the region on the front side in the rotation direction in the unit region on the first seal fin, the flow direction of the swirl flow and the first seal fin The position where the penetrating portion is provided can be made to correspond. Thereby, a swirl flow can be smoothly led to the penetration portion.

  According to the third aspect of the present invention, in the sealing device, the penetrating portion may be formed in a radially outer region of the first seal fin in the unit region.

  According to this configuration, since the through portion is formed in the radially outer region of the unit region on the first seal fin, the space between the first seal fin and the second seal fin is formed through the through portion. The introduced steam can be actively guided toward the swirl breaker provided in the space. That is, the swirl breaker can sufficiently function by forming the through portion.

  According to the fourth aspect of the present invention, in the above sealing device, the swirl breaker is seen from the radial direction of the axis, and the front side in the rotational direction of the rotating body as it goes from one side of the axis to the other side. It may extend toward the rear side.

  According to this configuration, the swirl breaker extends from the front side in the rotational direction toward the rear side as it goes from one side of the axis to the other side. That is, the angle formed by the direction in which the swirl breaker extends and the flow direction of the swirl flow can be made closer to a right angle. Thereby, the swirl flow can be sufficiently blocked by the swirl breaker.

  According to the fifth aspect of the present invention, in the sealing device, the dimension of the through portion in the radial direction of the axis is between the first seal fin in the radial direction of the axis and the outer peripheral surface of the rotating body. It may be set larger than the separation dimension.

  According to this configuration, the possibility that the swirl flow flows between the first seal fin and the outer peripheral surface of the rotating body is reduced, and the swirl flow can be smoothly guided by the penetrating portion.

  According to a sixth aspect of the present invention, in the sealing device, the penetrating portion is a unit region defined by a pair of swirl breakers adjacent in the circumferential direction on the first seal fin. A first through hole formed in a relatively radially outer region of the unit region, and a second through hole formed in a relatively radially inner region, wherein the first through hole has an axis The second through-hole extends from one side to the other side in the axial direction and extends from the rear side to the front side in the rotational direction of the rotating body. You may extend toward the back side from the direction front side.

  According to this structure, the vapor | steam which passed the 1st through-hole located in the radial direction outer side flows toward the front side from the rotation direction rear side of a rotary body as it goes to the other side from the axial direction. On the other hand, the vapor | steam which passed the 2nd through-hole located in the radial inside flows from the rotation direction front side toward the back side as it goes to the other side from the axial direction. Thereby, in the space formed between the first seal fin and the second seal fin, a vortex that flows clockwise as viewed from one side in the axial direction is formed. That is, in the vicinity of the outer peripheral surface of the rotating body (in the vicinity of the radially inner end of the first seal fin or the second seal fin), the flow direction of the vortex and the flow of the swirl flow as viewed from one side in the axial direction. The directions are in opposition to each other. Therefore, according to said structure, a swirl flow can be reduced by the flow of the vortex formed by the 1st through-hole and the 2nd through-hole.

  A rotating machine according to a seventh aspect of the present invention includes the rotor as the rotating body, the casing, and the sealing device according to any one of the above aspects.

  According to this configuration, a rotating machine in which the self-excited vibration of the rotor is sufficiently reduced can be obtained based on sufficient sealing performance and swirl reduction performance.

  ADVANTAGE OF THE INVENTION According to this invention, while having sufficient sealing performance, the sealing device which can reduce a swirl, and a rotary machine can be provided.

It is a mimetic diagram showing composition of a rotary machine (steam turbine) concerning a first embodiment of the present invention. It is a principal part expanded sectional view of the rotary machine which concerns on 1st embodiment of this invention, Comprising: It is a figure which shows the structure of a sealing device. It is sectional drawing which looked at the sealing apparatus which concerns on 1st embodiment of this invention from the radial direction outer side of the axis line. It is the figure which looked at the sealing device which concerns on 1st embodiment of this invention from the axial direction one side. It is sectional drawing which looked at the sealing apparatus which concerns on 2nd embodiment of this invention from the radial direction outer side of the axis line. It is the figure which looked at the sealing device which concerns on 3rd embodiment of this invention from the axial direction one side. It is the figure which looked at the sealing device which concerns on 4th embodiment of this invention from the axial direction one side. It is sectional drawing which looked at the sealing apparatus which concerns on 4th embodiment of this invention from the radial direction outer side of an axis, (a) is an AA arrow directional view of FIG. 7, (B) is FIG. It is a BB line arrow directional view.

[First embodiment]
A first embodiment of the present invention will be described with reference to the drawings. As shown in FIG. 1, a steam turbine 1 (rotary machine) according to the present embodiment includes a rotor 2 (rotating body) that rotates about an axis Ac, a casing 3 that covers the rotor 2 from the outer peripheral side, a rotor 2, and the like. And a sealing device 4 provided between the casing 3 and the casing 3.

  The rotor 2 is a columnar member extending along the axis Ac, and is supported by journal bearings 5 and thrust bearings 6 at the ends on both sides in the axis Ac direction. The rotor 2 has a plurality of blade stages 7 arranged on the outer peripheral surface thereof at intervals in the axis Ac direction. Each blade stage 7 has a plurality of blades arranged on the outer peripheral surface of the rotor 2 at intervals in the circumferential direction of the axis line Ac.

  On the inner peripheral surface of the casing 3, there are provided a plurality of stationary blade stages 8 arranged so as to be staggered in the axis line Ac direction with respect to the moving blade stage 7. In other words, the stationary blade stages 8 and the moving blade stages 7 are alternately arranged from one side to the other side in the axis Ac direction. These stationary blade stages 8 have a plurality of stationary blades arranged on the inner peripheral surface of the casing 3 at intervals in the circumferential direction of the axis line Ac.

  An intake port 9 for guiding high-temperature and high-pressure steam supplied from the outside to the inside of the casing 3 is formed on one side in the axis Ac direction of the casing 3. Further, an exhaust port 10 for exhausting the steam that has passed through the casing 3 is formed on the other side of the casing 3 in the axis Ac direction.

  Furthermore, in a gap (clearance) formed between the inner peripheral surface of the casing 3 and the radially outer end of the rotor blade, steam flowing from one side to the other side in the axis Ac direction through the clearance ( A sealing device 4 is provided to block the leaked steam).

  In the steam turbine 1 configured as described above, the steam guided into the casing 3 through the intake port 9 sequentially collides with each blade stage 7 and each stationary blade stage 8. Thereby, the rotor 2 is rotationally driven around the axis line Ac by the energy of the steam. The rotational energy of the rotor 2 is taken out by a generator (not shown) connected to the shaft end and used for power generation or the like. 2 and 4 referred to in the following description, the direction in which the rotor 2 rotates is denoted as Dr. Specifically, in this embodiment, the rotor 2 rotates clockwise as viewed from one side in the axis Ac direction.

  Next, a detailed configuration of the sealing device 4 will be described with reference to FIGS. As shown in FIG. 2, the sealing device 4 according to the present embodiment includes a plurality of seal fins 11 arranged on the inner peripheral surface of the casing 3 at intervals in the axis Ac direction, and between the seal fins 11. And a swirl breaker 12 provided in the.

  More specifically, each seal fin 11 extends from the inner peripheral surface of the casing 3 toward the inside in the radial direction of the axis Ac. Each seal fin 11 has an annular shape by spreading in the circumferential direction of the axis line Ac on the inner peripheral surface of the casing 3. In the present embodiment, a total of three seal fins 11 are opposed to one moving blade stage 7 from the radially outer side. Each seal fin 11 is formed so as to gradually taper from the radially outer side toward the inner side. In addition, a constant gap is formed between the tips (radially inner ends) of the seal fins 11 and the outer peripheral surface of the rotor 2 (radial blade radially outer ends).

  In the following description, among these three seal fins 11, the seal fin 11 located on the most one side in the axis Ac direction is referred to as a first seal fin 11A. Furthermore, the seal fin 11 adjacent to the first seal fin 11A on the other side in the axis Ac direction is referred to as a second seal fin 11B.

  A plurality of swirl breakers 12 are provided between the first seal fin 11A and the second seal fin 11B. The swirl breaker 12 connects the first seal fin 11A and the second seal fin 11B in the direction of the axis line Ac. More specifically, as shown in FIG. 3, each swirl breaker 12 has a plate-like shape arranged between the first seal fin 11 </ b> A and the second seal fin 11 </ b> B at intervals in the circumferential direction of the axis line Ac. It is a member. As shown in FIG. 4, each swirl breaker 12 extends in parallel with the radial direction of the axis Ac when viewed from one side in the axis Ac direction. As shown in FIGS. 2 and 4, the radially inner end of each swirl breaker 12 is positioned slightly radially outward from the radially inner end of the first seal fin 11 </ b> A. Here, an area defined by a pair of swirl breakers 12 adjacent in the circumferential direction on the first seal fin 11A is referred to as a “unit area S”. In other words, a plurality of unit regions S are arranged in the circumferential direction on the first seal fin 11A.

  Each unit region S is formed with a through portion 13 that penetrates the first seal fin 11A in the direction of the axis Ac. More specifically, as illustrated in FIG. 4, the through portion 13 is a through hole that is opened in a rectangular shape when viewed from the direction of the axis Ac. The penetrating portion 13 is located in an upper right region in the unit region S when viewed from one side in the axis Ac direction. In other words, the penetrating part 13 is formed at a position in the unit region S that is deviated forward of the rotational direction Dr and radially outward of the axis Ac. Furthermore, the dimension of the penetration part 13 in the radial direction of the axis line Ac is set to be larger than the separation dimension between the first seal fin 11A and the outer peripheral surface of the rotor 2 (the end part on the radially outer side of the rotor blade). .

  Next, operations of the steam turbine 1 and the seal device 4 according to the present embodiment will be described. As described above, in the steam turbine 1, the rotor 2 is rotationally driven by the high-temperature and high-pressure steam guided from the outside. As the rotor 2 rotates, a swirl flow (swirl flow) that swirls in the rotation direction Dr of the rotor 2 is formed in a gap (clearance) formed between the casing 3 and the rotor 2 (moving blade). . More specifically, the swirl flow spirally flows from the rear side in the rotational direction Dr to the front side as it goes from one side to the other side in the axis Ac direction. It is known that when such a swirl flow develops, a whirling vibration (self-excited vibration) of the rotor 2 occurs.

  Therefore, the steam turbine 1 according to the present embodiment is provided with a swirl breaker 12 that connects the first seal fin 11A and the second seal fin 11B in the axis Ac direction. By providing the swirl breaker 12, the above-described swirl flow can be blocked. That is, it is possible to suppress the self-excited vibration of the rotor 2 that occurs due to inadvertent development of the swirl flow.

  Furthermore, according to said structure, since the penetration part 13 is formed in the 1st seal fin 11A, a swirl flow is passed between the 1st seal fin 11A and the second seal fin 11B through the penetration part 13. You can actively lead to space. That is, by providing the penetration part 13, the swirl breaker 12 can fully function. On the other hand, if the through-hole 13 is not formed as described above, the swirl breaker 12 has a great resistance to the flow of steam, so that the steam avoids the swirl breaker 12 and the first seal fin 11A and the rotor. 2 may flow into the gap between the two outer peripheral surfaces. In other words, the purpose of sealing the steam flow cannot be sufficiently achieved. However, according to the above configuration, such a possibility can be reduced.

  The swirl flow is generated as the rotor 2 rotates. That is, this swirl flow flows from the rear side in the rotational direction Dr of the rotor 2 toward the front side as it goes from one side to the other side in the axis Ac direction. For this reason, according to the above configuration, since the through portion 13 is formed in the region in front of the rotation direction Dr in the unit region S on the first seal fin 11A, the swirl flow direction and The position where the penetrating portion 13 is provided on the first seal fin 11A can be made to correspond. Thereby, a swirl flow can be smoothly guided to the penetration portion 13.

  In addition, according to the above configuration, since the through portion 13 is formed in the radially outer region of the unit region S on the first seal fin 11A, the first seal fin 11A and the first seal fin 11A are arranged through the through portion 13. The steam guided to the space between the two seal fins 11B can be positively guided toward the swirl breaker 12 provided in the space. That is, the swirl breaker 12 can sufficiently function by forming the through portion 13.

  In particular, in the sealing device 4 described above, the dimension of the through portion 13 in the radial direction of the axis line Ac is between the first seal fin 11A and the outer peripheral surface of the rotor 2 (tip portion of the moving blade) in the radial direction of the axis line Ac. It is set larger than the separation dimension. Thereby, the possibility that the swirl flow flows between the first seal fin 11 </ b> A and the tip of the moving blade is reduced, and the swirl flow can be smoothly guided by the through-hole 13.

  In the above-described embodiment, the example in which the penetrating portion 13 is an opening provided in a region outside the radial direction in the unit region S and in front of the rotation direction Dr as viewed from one side in the axis Ac direction has been described. However, the aspect of the penetrating portion 13 is not limited to the above. For example, as shown in FIG. 5, almost all of the region on the front side in the rotation direction Dr in the unit region S may be penetrated in the axis Ac direction. According to such a configuration, it is possible to obtain the same operational effects as the above-described embodiment, and further simplify the processing to be performed on the first seal fin 11A.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIG. In addition, about the structure similar to said 1st embodiment, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted. As shown in the figure, in the sealing device 24 according to the present embodiment, the configuration of the swirl breaker 22 is different from the swirl breaker 12 in the first embodiment. More specifically, the swirl breaker 22 extends obliquely with respect to the axis Ac as viewed from the radial direction of the axis Ac. In other words, the swirl breaker 22 extends from the front side to the rear side in the rotational direction Dr of the rotor 2 as it goes from one side to the other side in the axis Ac direction.

As described in the first embodiment, a swirl flow that turns in the same direction as the rotation direction Dr of the rotor 2 is formed on one side in the axis Ac direction of the first seal fin 11A. This swirl flow collides with the swirl breaker 22 after passing through the penetration 13.
Here, the swirl breaker 22 extends from the rear side in the rotational direction Dr toward the front side as it goes from one side of the axis Ac to the other side. That is, the angle formed by the direction in which the swirl breaker 22 extends and the flow direction of the swirl flow can be made closer to a right angle. Thereby, the swirl flow can be sufficiently blocked by the swirl breaker 22.

  It is desirable that the angle (inclination angle α) formed by the swirl breaker 22 with respect to the axis Ac when viewed from the radial direction is appropriately set according to the swirl angle β of the swirl flow obtained by measurement or the like. For example, when the turning angle β is relatively large, the inclination angle α of the swirl breaker 22 is desirably set to a relatively small value. On the other hand, when the turning angle β is relatively small, it is desirable to set the inclination angle α of the swirl breaker 22 to a relatively large value. More generally, the sum (α + β) of the tilt angle α and the turning angle β is preferably in the range of 70 to 110 °, and preferably in the range of 80 to 100 °. More desirable. Most preferably, the value of (α + β) is 90 °.

  In the present embodiment, an example has been described in which the swirl breaker 22 has a plate shape extending linearly when viewed from the radial direction. However, the aspect of the swirl breaker 22 is not limited to this, and the swirl breaker 22 may have an airfoil cross section as viewed from the radial direction, for example. Even with such a configuration, it is possible to obtain the same functions and effects as in the above embodiments.

[Third embodiment]
Next, a third embodiment of the present invention will be described with reference to FIGS. In addition, about the structure similar to said each embodiment, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted. As shown in FIG. 7, in the sealing device 34 according to the present embodiment, as the through portion 32, two through holes (the first one arranged in the unit region S of the first seal fin 11 </ b> A with a radial interval therebetween. A through hole 32A and a second through hole 32B) are formed.

  The first through hole 32A is formed in a relatively radially outer region within the unit region S. The second through hole 32B is formed in a relatively radially inner region in the unit region S. Further, a line connecting the inlet side end portions (end portions on one side in the axis Ac direction) of the first through holes 32A and the second through holes 32B is parallel to the radial direction with respect to the axis Ac. In other words, on one side in the axis line Ac direction of the first seal fin 11A, the inlet side end portion of the first through hole 32A and the inlet side end portion of the second through hole 32B are formed at the same position in the circumferential direction. ing. Furthermore, the inlet side end portion of the first through hole 32A and the inlet side end portion of the second through hole 32B are located in the center in the circumferential direction in the unit region S.

  The first through hole 32A and the second through hole 32B extend while being inclined with respect to the axis line Ac as viewed from the radial direction. More specifically, as shown in FIG. 8A, the first through hole 32A extends from the rear side in the rotational direction Dr of the rotor 2 toward the front side as it goes from one side to the other side in the axis Ac direction. Yes. On the other hand, as shown in FIG. 8B, the second through hole 32B extends from the front side to the rear side in the rotational direction Dr of the rotor 2 as it goes from one side to the other side in the axis Ac direction. Thus, on the other side in the axis Ac direction of the first seal fin 11A, the outlet side end portions of the first through hole 32A and the second through hole 32B are formed at different positions in the circumferential direction. In the present embodiment, both the first through hole 32A and the second through hole 32B have a rectangular cross-sectional shape.

  According to such a configuration, the steam that has passed through the first through hole 32A located on the radially outer side moves from the rear side in the rotational direction Dr of the rotor 2 toward the front side as it goes from one side to the other side in the axis Ac direction. Flowing. On the other hand, the steam that has passed through the second through hole 32B located on the radially inner side flows from the front side toward the rear side in the rotational direction Dr as it goes from one side to the other side in the axis Ac direction. Thereby, in the space formed by the first seal fin 11A and the second seal fin 11B and the pair of swirl breakers 12 adjacent to each other in the circumferential direction, a vortex that flows clockwise as viewed from one side in the axis Ac direction is formed. Is done. That is, in the vicinity of the outer peripheral surface of the rotating body (near the end portion on the radially inner side of the first seal fin 11A or the second seal fin 11B), the swirl flow direction and the swirl direction as viewed from one side in the axis Ac direction. The flow direction is opposite to each other. Therefore, according to the above configuration, the swirl flow can be reduced by the vortex flow formed by the first through hole 32A and the second through hole 32B.

The embodiments of the present invention have been described above with reference to the drawings. Various modifications can be made without departing from the gist of the present invention.
In the first and third embodiments, the example in which both the first through hole 32A and the second through hole 32B have a rectangular cross-sectional shape has been described. However, the modes of the first through hole 32A and the second through hole 32B are not limited to the above, and may have, for example, a circular or elliptical cross-sectional shape.

DESCRIPTION OF SYMBOLS 1 ... Steam turbine 2 ... Rotor 3 ... Casing 4 ... Sealing device 5 ... Journal bearing 6 ... Thrust bearing 7 ... Moving blade stage 8 ... Stator blade stage 9 ... Intake port 10 ... Exhaust port 11 ... Seal fin 12 ... Swirl breaker 11A ... 1st seal fin 11B ... 2nd seal fin 13 ... penetration part 24 ... sealing device 22 ... swirl breaker 34 ... sealing device 32 ... penetration part 32A ... first penetration hole 32B ... second penetration hole Ac ... axis Dr ... rotation direction S ... Unit area

Claims (7)

A sealing device that seals a flow of fluid flowing from one side to the other side in the axial direction between an outer peripheral surface of a rotating body that can rotate around an axis and a casing that covers the rotating body from the outer peripheral side,
A plurality of seal fins that extend from the inner peripheral surface of the casing toward the radially inner side of the axial line, and are arranged in the axial direction;
Of the plurality of seal fins, a first seal fin positioned closest to one side in the axial direction and a second seal fin provided adjacent to the other side in the axial direction of the first seal fin are connected in the axial direction. A plurality of swirl breakers arranged at intervals in the circumferential direction,
With
A sealing device in which the first seal fin is formed with a penetrating portion penetrating the first seal fin in the axial direction.   The penetrating portion is formed in a region on the front side in the rotational direction of the rotating body among unit regions defined by a pair of swirl breakers adjacent in the circumferential direction on the first seal fin. 2. The sealing device according to 1.   The sealing device according to claim 2, wherein the penetrating portion is formed in a radially outer region of the first seal fin in the unit region.   4. The swirl breaker according to claim 1, wherein the swirl breaker extends from the front side to the rear side in the rotational direction of the rotating body as viewed from the radial direction of the axis toward the other side. The sealing device according to one item.   The dimension of the said penetration part in the radial direction of an axis is set larger than the separation dimension between said 1st seal fin and the outer peripheral surface of the said rotary body in the radial direction of an axis. The sealing device according to one item. The through portion is formed on the first seal fin in a relatively radially outer region of the unit region among the unit regions defined by the pair of swirl breakers adjacent in the circumferential direction. A first through hole and a second through hole formed in a relatively radially inner region,
The first through-hole extends from the rear side in the rotational direction of the rotating body toward the front side from the one side in the axial direction toward the other side,
5. The sealing device according to claim 1, wherein the second through hole extends from the front side to the rear side in the rotational direction of the rotating body as it goes from one side in the axial direction to the other side. A rotor as the rotating body;
The casing;
A sealing device according to any one of claims 1 to 6;
Rotating machine with

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