WO2018110695A1 - Dispositif de joint pour arbre, et machine tournante - Google Patents

Dispositif de joint pour arbre, et machine tournante Download PDF

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Publication number
WO2018110695A1
WO2018110695A1 PCT/JP2017/045070 JP2017045070W WO2018110695A1 WO 2018110695 A1 WO2018110695 A1 WO 2018110695A1 JP 2017045070 W JP2017045070 W JP 2017045070W WO 2018110695 A1 WO2018110695 A1 WO 2018110695A1
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WO
WIPO (PCT)
Prior art keywords
seal
shaft
rotating shaft
seal device
pressure side
Prior art date
Application number
PCT/JP2017/045070
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English (en)
Japanese (ja)
Inventor
誠司 佐部利
伸一郎 得山
Original Assignee
三菱重工コンプレッサ株式会社
三菱重工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱重工コンプレッサ株式会社, 三菱重工業株式会社 filed Critical 三菱重工コンプレッサ株式会社
Publication of WO2018110695A1 publication Critical patent/WO2018110695A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/102—Shaft sealings especially adapted for elastic fluid pumps
    • F04D29/104—Shaft sealings especially adapted for elastic fluid pumps the sealing fluid being other than the working fluid or being the working fluid treated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/44—Free-space packings
    • F16J15/447—Labyrinth packings

Definitions

  • the present invention relates to a shaft seal device and a rotary machine.
  • This application claims priority based on Japanese Patent Application No. 2016-244216 for which it applied to Japan on December 16, 2016, and uses the content here.
  • a rotary machine such as a centrifugal compressor generally has a gap between a rotary shaft and a stationary member such as a casing around the rotary shaft. Therefore, in many cases, a seal device that suppresses the outflow of the working fluid is provided in the gap between the outer peripheral surface of the rotating shaft and the stationary member.
  • the sealing device is provided at a cap part at the inlet of the impeller, between each stage of the multistage impeller, and at a balance piston part provided at the final stage of the multistage impeller.
  • a labyrinth seal and a damper seal as shown in Patent Document 1 below are known.
  • the labyrinth seal described above has a large number of annular seal fins in the gap between the outer peripheral surface of the rotating shaft and the stationary member, and fluid leakage is reduced by the pressure loss of the fluid flowing through the clearance between the tips of these seal fins.
  • the damper seal includes a hole pattern seal (see, for example, Patent Document 1), a honeycomb seal, and the like.
  • the hole pattern seal is a ring-shaped stationary member arranged with a gap from the rotating shaft, and a plurality of holes are formed on the facing surface facing the rotating shaft. It is possible to attenuate energy and reduce fluid leakage, and has a characteristic of providing a large damping effect.
  • the inventors in the hole pattern seal as shown in Patent Document 1, have a hole under the condition that a reverse swirl mechanism such as a shunt hole for reducing the flow of the circumferential component of the rotating shaft in the fluid is provided.
  • a reverse swirl mechanism such as a shunt hole for reducing the flow of the circumferential component of the rotating shaft in the fluid.
  • the present invention has been made in view of the above-described problems, and an object of the present invention is to provide a shaft seal device and a rotary machine capable of reducing a leakage flow rate while exhibiting a damping effect in a fluid.
  • a shaft seal device is disposed between a high pressure side region and a low pressure side region, and is between an outer peripheral surface of a rotating shaft and a stationary member provided on the outer peripheral side of the rotating shaft.
  • An annular seal having a cylindrical sealing surface facing the outer circumferential surface in the circumferential direction and an axial position different from that of the annular seal and projecting from one of the stationary member and the rotating shaft toward the other And a labyrinth seal having a plurality of seal fins.
  • the swirl suppression unit generates a reverse swirl flow that rotates in a direction opposite to the rotation direction of the rotation shaft, thereby damping the shaft swirl vibration provided at the seal inlet on the swirl suppression unit side of the annular seal.
  • the effect can be enhanced.
  • the labyrinth seal is provided in series with the annular seal in the axial direction in the gap between the outer peripheral surface of the rotating shaft and the stationary member, the fluid leakage flow rate can be reduced and the sealing performance is improved. Can be achieved.
  • the damping effect in a fluid and the leakage flow volume reduction effect can be made compatible. Therefore, fluid can be prevented from leaking from the high pressure side to the low pressure side in the axial direction through the gap between the rotating shaft and stationary member of the rotating machine provided with the shaft seal device, and the efficiency of the rotating machine can be reduced. Can be increased.
  • the annular seal is disposed on a higher pressure side than the labyrinth seal in the axial direction.
  • the plurality of seal fins of the labyrinth seal may be provided on the stationary member and protrude toward the rotating shaft.
  • the labyrinth seal can be attached to the stationary member together with the annular seal integrally or separately, so that there is an advantage that processing on the rotating shaft is unnecessary.
  • a rotating machine includes the shaft seal device according to any one of (1) to (3) above.
  • FIG. 1 is a cross-sectional view showing a schematic configuration of a rotating machine in an embodiment of the present invention.
  • FIG. 2 is a cross-sectional view showing the configuration of the shaft seal device of the rotary machine shown in FIG.
  • FIG. 3 is a partially broken perspective view of the casing provided with the shaft seal device.
  • 4 is a cross-sectional view taken along the line XI-XI shown in FIG. 2, and is a cross-sectional view showing a shunt hole provided in the rotating machine.
  • FIG. 5 is a cross-sectional view taken along line XII-XII shown in FIG. 2, and is a cross-sectional view showing the configuration of the annular seal.
  • 6 is a cross-sectional view taken along the line XIII-XIII shown in FIG. 2, and is a cross-sectional view showing the configuration of the labyrinth seal.
  • FIG. 7 is a cross-sectional view illustrating a configuration of a shaft seal device for a rotary machine
  • the shaft seal device 20 is provided in a rotary machine 1 including a multistage centrifugal compressor including a plurality of impellers 4.
  • the rotating machine 1 includes a rotating shaft 2, a bearing 3, an impeller 4, a shaft sealing device 20, and a casing 6 (stationary member).
  • the rotating shaft 2 has a columnar shape and extends in the central axis P direction (axial direction), and is rotatably supported by the bearing 3 at both ends in the central axis P direction.
  • One bearing 3 is provided at each end of the rotating shaft 2, and supports the rotating shaft 2 so as to be rotatable around the central axis P.
  • Each of these bearings 3 is attached to a casing 6.
  • the impeller 4 is attached to the rotating shaft 2 and compresses the process gas G (fluid) by using a centrifugal force generated by rotation integrally with the rotating shaft 2.
  • the impeller 4 is a so-called closed impeller 4 including a disk 4a, a blade 4c, and a cover 4b.
  • the disks 4a are each formed in a disk shape that gradually increases in diameter toward the outer side in the radial direction of the central axis P toward the central position C in the central axis P direction on the rotary shaft 2.
  • the blade 4c is formed so as to protrude from the disk 4a to the end side opposite to the central position C in the central axis P direction.
  • a plurality of blades 4c are formed at predetermined intervals in the circumferential direction of the central axis P.
  • the cover 4b covers the plurality of blades 4c from the end side in the central axis P direction.
  • the cover 4b is formed in a disk shape facing the disk 4a.
  • a plurality of impellers 4 are attached to the rotating shaft 2 between the bearings 3 arranged on both sides in the direction of the central axis P.
  • These impellers 4 constitute two sets of three-stage impeller groups 4A and 4B in which the direction of the blade 4c faces opposite to each other in the central axis P direction.
  • the pressure of the process gas G on the central position C side in the central axis P direction is the highest. That is, the process gas G flows while being compressed stepwise through the three-stage impeller group 4A and the three-stage impeller group 4B toward the central position C in the direction of the central axis P.
  • the casing 6 supports the bearing 3 and covers the rotating shaft 2, the impeller 4, and the shaft seal device 20 from the outer peripheral side.
  • the casing 6 is formed in a cylindrical shape.
  • the casing 6 includes a suction port 6bA on one side in the central axis P direction (left side in FIG. 1).
  • the suction port 6bA is connected to a suction channel 6cA formed in an annular shape.
  • the suction flow path 6cA is connected to the flow path of the impeller 4 disposed near the bearing 3 farthest from the center position C in the central axis P direction in the three-stage impeller group 4A. That is, the process gas G flowing from the suction port 6bA is introduced into the three-stage impeller group 4A via the suction flow path 6cA.
  • the casing 6 includes casing flow paths 6aA and 6aB that connect the flow paths formed between the blades 4c of the impellers 4 to each other.
  • the casing 6 includes a discharge port 6eA on the central position C side in the direction of the central axis P.
  • the discharge port 6eA is connected to a discharge channel 6dA formed in an annular shape.
  • the discharge flow path 6dA is connected to the flow path of the impeller 4 arranged closest to the center position C in the direction of the central axis P in the three-stage impeller group 4A. That is, the process gas G compressed by the impeller 4 disposed closest to the center position C in the direction of the central axis P in the three-stage impeller group 4A is discharged from the outlet 6eA to the outside of the casing 6 through the discharge passage 6dA. To be discharged.
  • the casing 6 is formed so that the first end portion side portion and the second end portion side portion centered on the center position C in the direction of the central axis P are symmetrical.
  • the casing 6 is formed with a casing channel 6aB, a suction port 6bB, a suction channel 6cB, a discharge channel 6dB, and a discharge port 6eB in a portion on the second end side of the center position C.
  • the process gas G discharged from the discharge port 6eA on the side of the three-stage impeller group 4A is sent to the suction port 6bB at a portion on the second end side of the center position C.
  • the process gas G flowing from the suction port 6bB is supplied to the three-stage impeller group 4B via the suction flow path 6cB and compressed in stages. In this way, the three-stage impeller group 4B further compresses the process gas G compressed by the three-stage impeller group 4A on the first end side.
  • the process gas G compressed by the three-stage impeller group 4B is discharged from the discharge port 6eB to the outside of the casing 6 through the discharge channel 6dB.
  • the three-stage impeller group 4B disposed in the portion closer to the second end than the center position C of the casing 6 has the three steps disposed in the portion closer to the first end than the center position C.
  • the process gas G compressed by the formula impeller group 4A is further compressed.
  • a pressure difference is generated between the three-stage impeller group 4A and the three-stage impeller group 4B.
  • the region where the three-stage impeller group 4A is arranged is a low-pressure side region where the pressure is low
  • the region where the three-stage impeller group 4B is arranged is a high-pressure side region where the pressure is high.
  • the rotary machine 1 has a gap g (see FIG. 2) formed between the outer peripheral surface 2a of the rotary shaft 2 and the inner peripheral surface of the casing 6 in the vicinity of the center position C.
  • the process gas G passes through the gap g between the outer peripheral surface 2a of the rotating shaft 2 and the inner peripheral surface of the casing 6 and travels from the high-pressure three-stage impeller group 4B side to the low-pressure three-stage impeller group 4B. Try to flow.
  • a shaft seal device 20 is provided to suppress the flow of process gas G from the high-pressure three-stage impeller group 4B toward the low-pressure three-stage impeller group 4B.
  • the shaft seal device 20 is disposed between the impellers 4 and provided along the outer peripheral surface 2 a of the rotating shaft 2.
  • the shaft seal device 20 is provided in the vicinity of a central position C between the high-pressure side three-stage impeller group 4B and the low-pressure side three-stage impeller group 4A.
  • the shaft seal device 20 seals the leakage of the process gas G between the outer peripheral surface 2 a of the rotating shaft 2 and the casing 6 provided on the outer peripheral side of the rotating shaft 2. It is arranged between the high-pressure side region (the high-pressure three-stage impeller group 4B side shown in FIG. 1) and the low-pressure side region (the low-pressure three-stage impeller group 4A side shown in FIG. 1).
  • the shaft seal device 20 is provided on the low pressure side of the shunt hole 30 and the shunt hole 30 for reducing the flow of the swirling component (circumferential component) of the rotating shaft 2 in the process gas G.
  • An annular seal 21 having a cylindrical seal surface 21a facing the outer circumferential surface 2a in the circumferential direction, and provided on the casing 6 at a lower pressure side than the annular seal 21 in the axial direction (direction along the central axis P).
  • a labyrinth seal 22 having a plurality of seal fins 22 ⁇ / b> B protruding toward the rotating shaft 2.
  • the shunt hole 30 is provided at one end (the first end portion on the left side of FIG. 2) on the high-pressure side in the central axis P direction with respect to the annular seal 21.
  • the shunt hole 30 includes a groove 31 that is continuous in the circumferential direction on the radially outer side of the rotating shaft 2, and a fluid supply path 32 that feeds the process gas G into the groove 31 from the radially outer side. And comprising.
  • a plurality of fluid supply paths 32 are provided on the outer side in the radial direction of the groove 31 with an interval in the circumferential direction.
  • Each fluid supply path 32 is inclined in the circumferential direction with respect to the radial direction around the central axis P, and feeds the process gas G into the groove 31 in a direction r2 opposite to the rotational direction r1 of the rotary shaft 2.
  • the process gas G fed into the groove 31 becomes a reverse swirl flow swirling in the direction r2 opposite to the rotation direction r1, flows into the gap g between the casing 6 and the rotation shaft 2, and is located at a lower pressure side than the shunt hole 30. It flows toward the other end in the central axis P direction where the annular seal 21 and the labyrinth seal 22 are provided (the second end side on the right side of FIG. 2).
  • the annular seal 21 has a cylindrical shape provided on the inner peripheral surface of the casing 6 with the rotary shaft 2 and the gap g.
  • the rotary shaft 2 is inserted into the annular seal 21.
  • the inner peripheral surface of the annular seal 21 is formed with a seal surface 21a that forms a smooth surface without unevenness (see FIG. 5).
  • the effect of damping the flow of the process gas G by the annular seal 21 is evaluated by equivalent damping (Cxx ⁇ Kxy / ⁇ ) using direct damping: Cxx and cross rigidity: Kxy (where ⁇ is the swing angle of the rotating shaft)
  • Cxx direct damping
  • Kxy cross rigidity
  • the process gas G flowing into the annular seal 21 has a swirl component in the same direction as the rotation direction r1 of the rotating shaft 2.
  • the swirl component of the process gas G increases the equivalent damping cross rigidity Kxy and lowers the equivalent damping value.
  • the cross rigidity Kxy is reduced by the reverse swirl flow fed from the shunt hole 30. Increase the equivalent attenuation.
  • the process gas G including the swirl is contracted by a gap g between the end portion on the highest pressure side of the annular seal 21 and the outer peripheral surface 2 a of the rotating shaft 2.
  • the process gas G that has entered the gap g swirls in the rotation direction r1 due to friction with the rotation shaft 2 rotating in the rotation direction r1, interference with the ring seal 21, and the like in the region where the ring seal 21 is disposed.
  • the speed of the process gas G flowing in the low pressure side along the direction of the central axis P in the reverse turning direction is reduced.
  • the labyrinth seal 22 is disposed on the inner peripheral surface of the casing 6 adjacent to the low pressure side of the annular seal 21 and has a cylindrical shape provided with the rotary shaft 2 and the gap g.
  • the rotary shaft 2 is inserted through the inside.
  • the labyrinth seal 22 has an annular outer peripheral cylinder 22A and a large number of seal fins 22B arranged on the inner peripheral surface of the outer peripheral cylinder 22A, and the process is caused by the pressure loss of the process gas G flowing through the clearance between the tips of the seal fins 22B.
  • the configuration is such that the leakage of the gas G is reduced.
  • the length of the annular seal 21 and the labyrinth seal 22 in the direction of the central axis P that is, the composition ratio is approximately half (1: 1 ratio) in FIG. 2, but is not limited thereto. It can be set appropriately.
  • the annular seal 21 and the labyrinth seal 22 are integrally formed by continuous parts, and the annular seal 21 and the labyrinth seal 22 are also provided integrally with the casing 6.
  • the annular seal 21 is generated by generating a reverse swirl flow that rotates in the direction opposite to the rotation direction of the rotating shaft 2 by the shunt hole 30. It is possible to suppress the swirling flow in the axial rotation direction flowing into the shaft and to make the flow in the direction opposite to the axial rotation. Thereby, the damping effect with respect to the whirling vibration of the shaft given at the seal inlet on the shunt hole 30 side of the annular seal 21 can be enhanced.
  • the labyrinth seal 22 is provided in series with the annular seal 21 and the central axis P direction in the gap g between the outer peripheral surface 2a of the rotating shaft 2 and the casing 6, the leakage flow rate of the process gas G is reduced. It is possible to improve the sealing performance.
  • the reverse swirl flow applied at the seal inlet is not weakened, and the damping effect with respect to the shaft whirling vibration in the annular seal 21 can be effectively applied.
  • the annular seal 21 having a high damping effect is disposed on the high pressure side where a large unstable fluid force is generally easily generated, the stability of the rotating shaft 2 can be improved.
  • the labyrinth seal 22 can be integrally or separately attached to the casing 6 together with the annular seal 21, so that there is an advantage that processing on the rotating shaft 2 becomes unnecessary.
  • the leakage flow rate can be reduced while exhibiting the damping effect in the process gas G.
  • the shunt hole 30 is targeted as the turning suppression unit, but is not limited to this.
  • the swirl suppression unit may suppress the swirl flow in the circumferential direction of the fluid (process gas G) accompanying the rotation of the rotating shaft 2.
  • it may be a swirl breaker or the like provided at an end portion on the inlet side (high pressure side) of the seal and having a plurality of convex portions arranged at intervals along the circumferential direction.
  • the annular seal 21 is arranged on the high pressure side with respect to the labyrinth seal 22 in the direction of the central axis P.
  • the annular seal 21 and the labyrinth seal 22 may be provided at different axial positions (directions along the central axis P).
  • the shaft seal device 20A according to the modification shown in FIG. 7 has a configuration in which the labyrinth seal 22 (22A, 22B) is disposed on the high-pressure side from the annular seal 21 in the central axis P direction.
  • the damping effect and the leakage flow rate reducing effect in the process gas G can be compatible, so that the efficiency of the rotating machine can be increased.
  • the labyrinth seal 22 is provided on the casing 6, that is, the stationary member side, but the labyrinth seal 22 may be provided on the rotating shaft 2. That is, it may be a labyrinth seal 22 having a plurality of seal fins that protrude from the rotary shaft 2 toward the stationary member on the outer side in the radial direction.
  • annular seal 21 and the labyrinth seal 22 are formed of continuous parts and are integrally provided in the casing 6 .
  • the present invention is not limited to this.
  • the annular seal 21 and the labyrinth seal 22 may be manufactured and combined with separate parts.
  • the annular seal 21 and the labyrinth seal 22 may be integrally formed, or may be a combination of parts divided in the circumferential direction, for example.
  • the shape, size, material, and the like of the annular seal 21 and the labyrinth seal 22 are not limited to the above-described embodiment, and can be arbitrarily set.
  • the shaft seal device and the rotary machine of the present invention it is possible to reduce the leakage flow rate while exhibiting the damping effect in the fluid.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un dispositif de joint (20) pour arbre, disposé entre une région côté haute pression et une région côté basse pression, le dispositif de joint (20) pour arbre empêchant de manière étanche les fuites d'un gaz de traitement (G) entre une face périphérique externe (2a) d'un arbre tournant (2) et un carter (6) agencé du côté périphérique externe de l'arbre tournant (2). Le dispositif de joint pour arbre comprend un trou de dérivation (30) destiné à réduire l'écoulement d'un constituant du gaz de traitement coulant dans la direction circonférentielle de l'arbre tournant (2), un joint annulaire (21) agencé sur le côté basse pression du trou de dérivation (30) et comportant une face de joint (21a) prenant la forme d'une face cylindrique en regard de la face périphérique externe (2a) de l'arbre tournant (2) tout au long de la direction circonférentielle, et un joint labyrinthe (22) disposé plus vers le côté basse pression que le joint annulaire (21) le long de la direction d'un axe central (P) et comportant une pluralité d'ailettes de joint (22B) faisant saillie à partir du carter (6) vers l'arbre tournant (2).
PCT/JP2017/045070 2016-12-16 2017-12-15 Dispositif de joint pour arbre, et machine tournante WO2018110695A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016244216A JP2018096514A (ja) 2016-12-16 2016-12-16 軸シール装置、及び回転機械
JP2016-244216 2016-12-16

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WO2018110695A1 true WO2018110695A1 (fr) 2018-06-21

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WO (1) WO2018110695A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109441869A (zh) * 2018-12-21 2019-03-08 成都成发科能动力工程有限公司 一种压缩机轴端组合密封机构

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0719005A (ja) * 1993-06-30 1995-01-20 Toshiba Corp ラビリンスシール装置
JP4655123B2 (ja) * 2008-08-07 2011-03-23 株式会社日立プラントテクノロジー 遠心圧縮機
WO2013115361A1 (fr) * 2012-02-03 2013-08-08 三菱重工業株式会社 Structure de joint d'étanchéité et machine rotative dotée de celle-ci
JP2014238066A (ja) * 2013-06-10 2014-12-18 三菱重工業株式会社 回転機械
JP2016180349A (ja) * 2015-03-24 2016-10-13 三菱重工業株式会社 回転機械

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0719005A (ja) * 1993-06-30 1995-01-20 Toshiba Corp ラビリンスシール装置
JP4655123B2 (ja) * 2008-08-07 2011-03-23 株式会社日立プラントテクノロジー 遠心圧縮機
WO2013115361A1 (fr) * 2012-02-03 2013-08-08 三菱重工業株式会社 Structure de joint d'étanchéité et machine rotative dotée de celle-ci
JP2014238066A (ja) * 2013-06-10 2014-12-18 三菱重工業株式会社 回転機械
JP2016180349A (ja) * 2015-03-24 2016-10-13 三菱重工業株式会社 回転機械

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