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WO2012001995A1 - Dispositif d'étanchéité et machine fluidique comprenant celui-ci - Google Patents

Dispositif d'étanchéité et machine fluidique comprenant celui-ci Download PDF

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Publication number
WO2012001995A1
WO2012001995A1 PCT/JP2011/051189 JP2011051189W WO2012001995A1 WO 2012001995 A1 WO2012001995 A1 WO 2012001995A1 JP 2011051189 W JP2011051189 W JP 2011051189W WO 2012001995 A1 WO2012001995 A1 WO 2012001995A1
Authority
WO
WIPO (PCT)
Prior art keywords
swirl
outer peripheral
sealing device
rotating body
pressure side
Prior art date
Application number
PCT/JP2011/051189
Other languages
English (en)
Japanese (ja)
Inventor
孝昌 平井
勝也 山下
Original Assignee
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 三菱重工業株式会社 filed Critical 三菱重工業株式会社
Publication of WO2012001995A1 publication Critical patent/WO2012001995A1/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
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • 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
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel
    • 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

Definitions

  • the present invention relates to a sealing device and a fluid machine including the same.
  • This application claims priority based on Japanese Patent Application No. 2010-146512 filed in Japan on June 28, 2010, the contents of which are incorporated herein by reference.
  • a seal portion that seals a radial gap formed between the casing and the rotating body is provided. It has been.
  • an impeller outer peripheral portion in the vicinity of an impeller inlet of each stage that is, an outer peripheral surface of a shroud disk, is composed of a rotating body provided in a plurality of stages in the axial direction and a housing that accommodates the rotating body.
  • a labyrinth seal is provided in a radial gap between the housing and the inner periphery of the housing (for example, see Patent Document 1 below).
  • the seal excitation force acting on the shaft vibration increases with the high pressure and high performance of the fluid machine, and the shaft system instability problem tends to become remarkable.
  • This excitation force is greatly influenced by a swirling flow (swirl) having a circumferential velocity component flowing along the outer periphery of the rotating body. That is, as a result of the swirling flow flowing into the seal portion, the natural frequency of the shaft system is excited, and the shaft vibration increases.
  • a sealing device in which a plurality of swirl breakers extending radially inward are provided on the high-pressure side of the labyrinth seal with an interval in the circumferential direction (for example, See Patent Document 2 below).
  • the fluid is decelerated to prevent an increase in vibration.
  • guide vanes are attached to a baffle plate attached to a swirl breaker along the flow direction of the swirl flow.
  • the tip of the swirl breaker is arranged with a slight gap from the rotating body. Therefore, the swirl flow can be interrupted in the range where the swirl breaker exists in the radial direction of the rotating body, while the swirling flow flows between the tip of the swirl breaker and the rotating body. As a result of the swirling flow reaching the seal portion, a seal excitation force acting on the shaft vibration is generated, and there is a problem that a sufficient vibration suppressing effect cannot be obtained.
  • the present invention has been made in view of such circumstances, and an object thereof is to provide a sealing device and a fluid machine that can stably obtain a vibration suppressing effect with a simple configuration.
  • the sealing device seals the radial gap of the rotating body formed between the casing and the outer peripheral surface of the rotating body that is rotatably disposed inside the casing so as to reduce the pressure from the high pressure side.
  • a seal portion that suppresses fluid flowing toward the side, and a fluid that extends from the casing toward the outer peripheral surface and flows through the gap in the circumferential direction of the rotating body on the high-pressure side of the seal portion A swirl breaker is provided, and a guide member for guiding the fluid outward in the radial direction is provided on the outer peripheral surface of the rotating body on the high pressure side of the swirl breaker.
  • the guide member guides the circumferential flow of the fluid along the outer peripheral surface of the rotating body, that is, the swirling flow to the outside in the radial direction, so that the swirl breaker, the rotating body, The swirling flow can be prevented from flowing in between.
  • the guide member may include a guide surface that gradually inclines toward the outside in the radial direction from the high pressure side toward the low pressure side.
  • the circumferential dimension of the guide member may be set larger than the circumferential dimension of the swirl breaker.
  • the swirl flow can be more effectively guided radially outward on the high pressure side of the swirl breaker.
  • the guide member may be formed in a ring shape extending over the entire circumferential direction.
  • a plurality of the guide members may be provided at intervals in the circumferential direction.
  • the guide member can effectively guide the swirl flow radially outward, and the guide member can be easily installed as compared with the case where the guide member has a ring shape. Therefore, productivity can be improved.
  • a plurality of the sealing portions are provided in the axial direction of the rotating body, the swirl breakers are provided on the high pressure sides of the sealing portions, respectively, and further, the high pressure sides of the swirl breakers are respectively provided.
  • the guide member may be provided.
  • the swirl flow generated on the low pressure side of the swirl breaker arranged on the highest pressure side is obtained by arranging a plurality of sets of seal parts, swirl breakers and guide members from the high pressure side to the low pressure side. It can suppress effectively and can obtain the stable vibration suppression effect as the whole shaft system.
  • a fluid machine includes a casing and a rotating body that is rotatably disposed in the casing, and the fluid machine in which the fluid flows in the casing includes any one of the above-described sealing devices.
  • the sealing device is provided.
  • the outer peripheral surface of the rotating body may be an outer peripheral surface of an impeller shroud.
  • the outer peripheral surface of the rotating body may be the outer peripheral surface of a balance piston.
  • vibration based on the swirling flow in the sealing device between the outer peripheral surface of the balance piston and the casing can be suppressed.
  • the swirling flow is prevented from flowing between the swirl breaker and the rotating body by guiding the swirling flow radially outward by the guide member. Can do. Thereby, it becomes possible to obtain the vibration suppression effect stably.
  • FIG. 2 is a cross-sectional view taken along line AA in FIG. It is an enlarged view of the sealing device in FIG. It is a schematic block diagram of the compressor provided with the sealing device which concerns on 2nd embodiment. It is an enlarged view of the sealing device in FIG. It is a principal part enlarged view of the compressor provided with the sealing device which concerns on 3rd embodiment. It is a figure explaining the example which applied the sealing device to the steam turbine.
  • FIGS. 1 to 3 An example in which the sealing device 1 is applied to a gap S between a shroud 17 of an impeller 14 and a casing 11 in a compressor (fluid machine) 10 is shown.
  • the compressor 10 includes a casing 11 and a rotating body 12 having a rotor shaft 13 and an impeller 14.
  • the casing 11 has a cylindrical shape that forms the appearance of the compressor 10, and a rotor shaft 13 is disposed inside the casing 11 so as to penetrate the center.
  • a rotor shaft 13 is disposed inside the casing 11 so as to penetrate the center.
  • radial bearings (not shown) and thrust bearings (not shown) are arranged on both sides of the casing 11.
  • the rotor shaft 13 is supported by the radial bearing and the thrust bearing, so that the rotating body 12 can rotate around the axis O.
  • the impeller 14 is a so-called closed impeller, and includes a hub 15, a plurality of blades 16, and a shroud 17.
  • the hub 15 is a cylindrical disk member, and is integrally fixed to the rotor shaft 13 so that the rotor shaft 13 penetrates coaxially.
  • the hub 15 has a shape that gradually increases in diameter from one side in the axis O direction (left side in FIG. 1) toward the other side in the axis O direction (right side in FIG. 1).
  • the blade 16 is a curved blade-like part, and extends from the outer peripheral surface 15a of the hub 15 toward the outer side of the axis O radial direction (hereinafter simply referred to as the radial direction), and is arranged along the outer peripheral surface 15a. Yes.
  • a plurality of blades 16 are provided in the circumferential direction of the axis O (hereinafter simply referred to as the circumferential direction).
  • the shroud 17 is a part formed in a cylindrical shape so as to cover the outer peripheral surface 15 a of the hub 15, and is connected to the outer peripheral side in the radial direction of each blade 16.
  • the outer peripheral surface 18 of the shroud 17 has a shape that gradually increases in diameter from one side in the direction of the axis O toward the other side.
  • a space defined between the hub 15, the shroud 17, and the blade 16 serves as a fluid flow path.
  • a portion opening toward the axis O direction on one side of the axis O direction is a gas inflow portion 14a, and a portion opening toward the radial direction on the other side of the axis O direction is a gas outflow portion 14b.
  • the casing 11 is provided with a suction port (not shown) for sucking fluid from the outside.
  • the fluid sucked into the suction port is changed in the direction of the axis O by passing through the suction flow path 11a and is introduced into the gas inflow portion 14a of the impeller 14.
  • the compressed fluid flowing out from the gas outflow portion 14 b is led out radially outward through the diffuser portion 11 b provided in the casing 11.
  • a gap S is formed between the shroud facing surface 11 c and the outer peripheral surface 18 of the shroud 17.
  • the gas outflow portion 14b side has a higher pressure than the gas inflow portion 14a side. Accordingly, in the gap S, fluid flows from the impeller 14 outlet side (gas outflow portion 14b side), which is the high pressure side, toward the impeller 14 inlet side (gas inflow portion 14a side), which is the low pressure side. And the sealing apparatus 1 of this embodiment is used in order to seal the clearance gap S through which the fluid distribute
  • the sealing device 1 is provided on one side of the gap S in the direction of the axis O, that is, on the low pressure side of the gap S, and includes a labyrinth seal (seal part) 2, a swirl breaker 3, and a swirl guide fin ( Guide member) 4.
  • the labyrinth seal 2 is configured by a plurality of annular fins 2a extending inward in the radial direction from the shroud facing surface 11c in the casing 11 in the axis O direction. Thereby, the labyrinth seal 2 seals the gap S and prevents the fluid from leaking from the other side in the axis O direction to the one side, that is, from the high pressure side to the low pressure side. Yes.
  • the swirl breaker 3 is a plate-like member that extends radially inward from the shroud facing surface 11c on the other side in the axis O direction of the labyrinth seal 2, that is, on the high pressure side, and is spaced apart in the circumferential direction of the axis O. There are a plurality of open spaces.
  • the swirl breaker 3 extends toward the outer peripheral surface 18 of the shroud 17, like the annular fin 2 a of the labyrinth seal 2.
  • the swirl guide fin 4 is provided on the outer peripheral surface 18 of the shroud 17 on the other side in the axis O direction of the swirl breaker 3, that is, on the high pressure side.
  • the swirl guide fin 4 is formed in a ring shape with the axis O as the center, and is integrally fixed to the outer peripheral surface 18 so as to extend over the entire outer peripheral surface 18 of the shroud 17.
  • the swirl guide fin 4 has a substantially triangular shape in a cross section including the axis O, and the guide surface 4 a facing the radially outer side of the swirl guide fin 4 is continuous with the outer peripheral surface 18, and the axis line
  • the diameter gradually increases toward the one side (low pressure side) in the O direction.
  • the guide surface 4 a is formed in a ring shape around the axis O according to the shape of the swirl guide fin 4.
  • the tip end of the guide surface 4a in the swirl guide fin 4 that is, the end portion located on the outermost radial direction side of the guide surface 4a reaches the outer side in the radial direction with respect to the tip end 3a of the swirl breaker 3.
  • the tip 3 a of the swirl breaker 3 enters a state radially inward from the tip of the guide surface 4 a in the swirl guide fin 4. That is, when the swirl breaker 3 is viewed from the direction of the axis O, the swirl breaker 3 and the swirl guide fin 4 overlap each other in the direction of the axis O.
  • the radial distance between the tip 3a of the swirl breaker 3 and the outer peripheral surface 18 and the distance in the direction of the axis O between the swirl breaker 3 and the swirl guide fin 4 are formed to be narrow so as to prevent the inflow of the swirl flow C described later. Is done.
  • the swirl guide fin 4 is provided on the high pressure side of the swirl breaker 3, the swirl flow C is guided radially outward by the guide surface 4a of the swirl guide fin 4. Accordingly, the swirl flow C can be guided toward the swirl breaker 3 so as to be separated from the outer peripheral surface 18, and the swirl flow C is prevented from flowing between the swirl breaker 3 and the outer peripheral surface 18. can do. Therefore, since it is possible to prevent the swirling flow C from reaching the labyrinth seal 2, the natural frequency of the shaft system is not excited, and the impeller 14 is stably rotated without vibration. It becomes possible.
  • the tip of the swirl guide fin 4 is positioned radially outside the tip 3a of the swirl breaker 3, so that the tip of the swirl guide fin 4 and the tip 3a of the swirl breaker 3 have a diameter. Separated in direction. Thereby, since the swirl flow C becomes difficult to reach the tip 3a of the swirl breaker 3, it is possible to further suppress the swirl flow C from flowing between the swirl breaker 3 and the outer peripheral surface 18.
  • the swirl guide fin 4 is formed in a ring shape centering on the axis O, the guide surface 4a of the swirl guide fin 4 exists over the entire outer circumferential surface 18 of the shroud 17 in the circumferential direction. ing. As a result, since all of the swirl flow C flowing along the outer peripheral surface 18 can be guided to the swirl breaker 3, the swirl flow C flows between the tip 3a of the swirl breaker 3 and the outer peripheral surface 18. It can prevent more reliably.
  • the sealing device 1 can be realized only by arranging the swirl guide fin 4 on the outer peripheral surface 18 of the shroud 17 that is relatively easy to change in design. it can. Therefore, it is possible to suppress the swirling flow C from flowing between the swirl breaker 3 and the outer peripheral surface 18 without making a major design change.
  • the sealing device 1 is applied to a gap S between a balance piston 29 and a casing 28 in a so-called back-to-back compressor (fluid machine) 20 is shown.
  • the compressor 20 of the present embodiment includes a rotor shaft 21, a low pressure section 22, a high pressure section 25, a balance piston (rotary body) 29, and a casing 28.
  • the rotor shaft 21 is rotatable about the axis O by supporting both ends of the rotor shaft 21 with a radial bearing (not shown) and a thrust bearing (not shown), for example.
  • the low pressure section 22 includes a low pressure side impeller 23 and a gas flow path 24 dug in the casing 28.
  • the low-pressure side impeller 23 has a gas passage defined by a hub, blades, and a shroud.
  • the gas passage has a rotor shaft 21 side as a gas inlet 23a and a side away from the rotor shaft 21 has a gas outlet 23b.
  • the low pressure side impeller 23 is arranged in a state where the gas inlet 23a is directed to one side of the axis O (left side in FIG. 4).
  • the gas flow path 24 includes a low pressure suction path 24a connecting a gas source (not shown) and a gas inlet 23a of the low pressure side impeller 23, and a low pressure discharge path 24b communicating from the gas outlet 23b of the low pressure side impeller 23 to the outside of the system. Yes.
  • the high pressure section 25 includes a high pressure side impeller 26 and a gas flow path 27 dug in the casing 28.
  • the high-pressure side impeller 26 has a gas passage defined by a hub, blades, and a shroud.
  • the gas passage 26 has a gas inlet 26a on the rotor shaft 21 side and a gas outlet 26b on the side away from the rotor shaft 21. Has been.
  • the high pressure side impeller 26 is arranged with the gas inlet 26a facing the other side of the axis O (the right side in FIG. 4).
  • the low-pressure side impeller 23 of the low-pressure section 22 and the high-pressure side impeller 26 of the high-pressure section 25 are disposed so as to face each other, and the compressor 20 disposed in this way is configured to be back-to-back (Back To Back). Back) type.
  • the gas flow path 27 includes a high-pressure suction path 27a that communicates gas introduced from the low-pressure discharge path 24b via a device such as an external intercooler to the gas inlet 26a of the high-pressure side impeller 26, and the high-pressure side impeller. And a high-pressure discharge passage 27b communicating from the gas outlet 26b to the outside of the system.
  • the balance piston 29 is provided between the low pressure section 22 and the high pressure section 25.
  • the balance piston 29 has a substantially cylindrical shape, and is fixed integrally with the rotor shaft 21 by being fitted on the outer peripheral side of the rotor shaft 21.
  • This balance piston 29 adjusts the load balance in the axis O direction of the rotor shaft 21 by resisting a load toward one side in the axis O direction caused by the pressure difference between the low pressure side impeller 23 and the high pressure side impeller 26.
  • the outer peripheral surface 30 of the balance piston 29 is a cylindrical surface centered on the axis O.
  • the surface of the casing 28 facing the outer peripheral surface 30 of the balance piston 29 is a piston facing surface 28a.
  • a gap S is formed between the outer peripheral surface 30 of the balance piston 29 and the piston facing surface 28 a of the casing 28.
  • the sealing device 1 is used to seal the gap S through which the fluid flows in this way.
  • the sealing device 1 of the second embodiment includes a labyrinth seal (seal part) 2, a swirl breaker 3, and a swirl guide fin (guide member) 4.
  • the labyrinth seal 2 is configured by a plurality of annular fins 2 a extending inward in the radial direction from the piston facing surface 28 a in the casing 28 in the axis O direction. Thereby, the labyrinth seal 2 seals the gap S and prevents the fluid from leaking from the other side in the axis O direction to the one side, that is, from the high pressure side to the low pressure side. Yes.
  • the swirl breaker 3 extends radially inward from the piston facing surface 28a, that is, toward the outer peripheral surface 18 of the shroud 17, on the other side in the axis O direction of the labyrinth seal 2, that is, on the high pressure side. A plurality are provided at intervals in the O circumferential direction.
  • the swirl guide fin 4 is provided on the outer peripheral surface 30 of the balance piston 29 on the other side in the axis O direction of the swirl breaker 3, that is, on the high pressure side.
  • the swirl guide fin 4 is formed in a ring shape with the axis O as the center, and is integrally fixed to the outer peripheral surface 30 so as to extend over the entire outer peripheral surface 30 of the balance piston 29.
  • the swirl guide fin 4 has a substantially triangular shape in a cross section including the axis O, and the guide surface 4a facing outward in the radial direction of the swirl guide fin 4 is directed to one side (low pressure side) in the axis O direction.
  • the diameter gradually increases according to
  • the guide surface 4 a is formed in a ring shape around the axis O according to the shape of the swirl guide fin 4.
  • the tip end of the guide surface 4a in the swirl guide fin 4 that is, the end portion located on the outermost radial direction side of the guide surface 4a is radially outward from the tip end 3a of the swirl breaker 3 as in the first embodiment.
  • the tip 3 a of the swirl breaker 3 enters a state radially inward from the tip of the guide surface 4 a in the swirl guide fin 4. That is, when the swirl breaker 3 is viewed from the direction of the axis O, the swirl breaker 3 and the swirl guide fin 4 overlap each other in the direction of the axis O.
  • the swirl guide fin 4 is provided on the high pressure side of the swirl breaker 3 as in the first embodiment, and therefore the swirl flow C is guided to the swirl guide fin 4. Guided radially outward by the surface 4a.
  • the swirl flow C can be guided toward the swirl breaker 3 so as to be separated from the outer peripheral surface 30 of the balance piston 29, and the swirl flow C flows between the swirl breaker 3 and the outer peripheral surface 18. Can be suppressed. Accordingly, since the swirling flow C can be prevented from reaching the labyrinth seal 2, the natural frequency of the shaft system is not excited, and the balance piston 29 is stably rotated without vibration. It becomes possible to make it.
  • the sealing device 40 of the third embodiment is disposed in the gap S between the balance piston 29 and the casing 28 in the compressor 20 as in the second embodiment.
  • the sealing device 1 according to the second embodiment has a configuration in which the single labyrinth seal 2, the swirl breaker 3, and the swirl guide fin 4 are arranged.
  • two labyrinth seals 2 (2A, 2B), swirl breakers 3 (3A, 3B) and swirl guide fins 4 (4A, 4B) are provided. That is, the labyrinth seal 2, the swirl breaker 3, and the swirl guide fin 4 are set as one set, and two sets are provided so as to be continuous in the direction of the axis O of the gap S.
  • the sealing device 40 of the third embodiment having such a configuration, the swirl flow entering from the high pressure side of the gap S is guided to the first swirl breaker 3A by the first swirl guide fin 4A. This prevents the swirling flow C from flowing into the first labyrinth seal 2A beyond the first swirl breaker 3A.
  • the fluid is accompanied by the rotation of the balance piston 29, so that the low pressure side of the first swirl breaker 3A, that is, the first labyrinth seal 2A.
  • a swirling flow C may occur between the outer circumferential surface 30 and the outer peripheral surface 30.
  • the second swirl breaker 3B is disposed on the low pressure side of the first labyrinth seal 2A, and the second swirl guide fin 4B is disposed immediately before the second swirl breaker 3B. Therefore, the swirl flow C can be guided to the second swirl breaker 3B by the second swirl guide fin 4B.
  • the labyrinth seal 2, the swirl breaker 3 and the swirl guide fin 4 are arranged in a plurality from the high pressure side to the low pressure side, so that the low pressure side of the swirl breaker 3 arranged on the highest pressure side is arranged. It is possible to effectively suppress the swirling flow generated in Therefore, even if the gap S in which the sealing device 40 is provided is formed long in the direction of the axis O, it is possible to effectively suppress the swirling flow C and obtain a stable vibration suppressing effect as the entire shaft system. .
  • the swirl guide fins 4 are ring-shaped extending over the entire circumferential direction, but the present invention is not limited to this.
  • the plurality of swirl guide fins 4 are spaced apart in the circumferential direction.
  • An arranged configuration may be used. This also allows the swirl flow C to be guided to the swirl breaker 3 as in the embodiment.
  • the productivity can be improved.
  • the circumferential dimension of the swirl guide fin 4 is set larger than the circumferential dimension of the swirl breaker 3. Thereby, the swirl flow C can be effectively guided to the swirl breaker 3.
  • a plurality of labyrinth seals 2, swirl breakers 3, and swirl guide fins 4 are provided, respectively, as in the third embodiment. Also good.
  • the labyrinth seal 2 may be provided on the rotating body side, that is, on the shroud 17 or the balance piston 29.
  • the sealing device 1 may be applied to a steam turbine.
  • a nozzle is incorporated in a partition plate 56 fixed to a casing 55, and a rotor shaft (rotary body) 51 is generated by a thrust force when steam passing through the nozzle passes through a moving blade. It is set as the structure which rotates.
  • a labyrinth seal 2 is provided between the casing 55 and the rotor shaft 51, and the swirl induction fin 4 is provided on the high pressure side of the labyrinth seal 2, that is, on the other side of the axis O (left side in FIG. 7). Is provided.
  • a swirl breaker 3 is provided between the labyrinth seal 2 and the swirl guide fin 4 so as to extend from the casing 55 toward the rotor shaft 51.
  • a sealing device 40 including a plurality of labyrinth seals 2, swirl breakers 3, and swirl guide fins 4 may be applied as in the third embodiment.
  • sealing devices 1 and 40 may be applied not only to the compressor and the steam turbine but also to other fluid machines such as a gas turbine, a water turbine, a refrigerator, and a pump.
  • a vibration suppressing effect can be stably obtained with a simple configuration.
  • Sealing device 2 Labyrinth seal (seal part) 2A Labyrinth seal (seal part) 2B Labyrinth seal (seal part) 2a annular fin 3 swirl breaker 3A swirl breaker 3B swirl breaker 3a tip 4 swirl guiding fin 4A swirl guiding fin 4B swirl guiding fin 4a guide surface 10 compressor 11 casing 11c shroud facing surface 12 rotor 13 rotor shaft 14 impeller 17 shroud 18 outer periphery Surface 20 Compressor 21 Rotor shaft 28 Casing 28a Piston facing surface 29 Balance piston 30 Outer peripheral surface 40 Sealing device 50 Steam turbine 51 Rotor shaft (rotating body) 55 casing

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

Abstract

L'invention concerne un dispositif d'étanchéité comprenant : une section d'étanchéité qui assure l'étanchéité d'un espace formé, dans la direction du diamètre d'un corps rotatif, entre un corps et la surface périphérique externe du corps rotatif qui est disposé de façon rotative à l'intérieur du corps, et qui commande le fluide qui s'écoule d'un côté haute pression vers un côté basse pression ; et un briseur de tourbillon à l'intérieur du côté haute pression de la section d'étanchéité, qui s'étend depuis le corps en direction de la surface périphérique externe et qui commande le fluide qui s'écoule à travers l'espace dans la direction circonférentielle du corps rotatif. Un élément de guidage qui guide le fluide vers l'extérieur de la direction de diamètre est disposé sur la surface circonférentielle externe du corps rotatif du côté haute pression du briseur de tourbillon.
PCT/JP2011/051189 2010-06-28 2011-01-24 Dispositif d'étanchéité et machine fluidique comprenant celui-ci WO2012001995A1 (fr)

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JP2010-146512 2010-06-28
JP2010146512A JP2012007592A (ja) 2010-06-28 2010-06-28 シール装置及びこれを備えた流体機械

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US20130142641A1 (en) * 2011-12-05 2013-06-06 Nuovo Pignone S.P.A. Turbomachine
WO2013132055A1 (fr) * 2012-03-08 2013-09-12 Siemens Aktiengesellschaft Turbomachine radiale comprenant un élément de réduction de tourbillonnement
CN103321950A (zh) * 2013-07-02 2013-09-25 台州豪贝泵业有限公司 一种泵用自适应性调节口环装置
WO2014004628A2 (fr) 2012-06-27 2014-01-03 Flowserve Management Company Dispositif anti-tourbillonnement
US20140201961A1 (en) * 2011-08-22 2014-07-24 Mitsubishi Rayon Co., Ltd. Steam Drawing Device
JP2015090144A (ja) * 2013-11-07 2015-05-11 三菱重工業株式会社 シール装置、および、回転機械
CN105283673A (zh) * 2013-05-03 2016-01-27 戴森技术有限公司 振动隔离安装件
JP2020101169A (ja) * 2018-12-25 2020-07-02 三菱重工業株式会社 遠心回転機械

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KR101501477B1 (ko) * 2013-03-25 2015-03-12 두산중공업 주식회사 원심압축기
KR102642363B1 (ko) * 2021-07-23 2024-03-04 엘지전자 주식회사 터보 압축기

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