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WO2014038080A1 - Dispositif de palier de butée et machine tournante utilisant celui-ci - Google Patents

Dispositif de palier de butée et machine tournante utilisant celui-ci Download PDF

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Publication number
WO2014038080A1
WO2014038080A1 PCT/JP2012/073030 JP2012073030W WO2014038080A1 WO 2014038080 A1 WO2014038080 A1 WO 2014038080A1 JP 2012073030 W JP2012073030 W JP 2012073030W WO 2014038080 A1 WO2014038080 A1 WO 2014038080A1
Authority
WO
WIPO (PCT)
Prior art keywords
thrust bearing
thrust
bearing device
runner
bearing plate
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2012/073030
Other languages
English (en)
Japanese (ja)
Inventor
智彬 山下
真 辺見
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Ltd
Original Assignee
Hitachi Ltd
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 Hitachi Ltd filed Critical Hitachi Ltd
Priority to PCT/JP2012/073030 priority Critical patent/WO2014038080A1/fr
Priority to JP2014534136A priority patent/JPWO2014038080A1/ja
Publication of WO2014038080A1 publication Critical patent/WO2014038080A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/02—Sliding-contact bearings
    • F16C25/04—Sliding-contact bearings self-adjusting
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/1085—Channels or passages to recirculate the liquid in the bearing

Definitions

  • the present invention relates to a bearing device that supports a rotating shaft of a rotating machine such as a steam turbine, and more particularly to a thrust bearing device that restricts the movement of the rotating shaft in the thrust direction and a rotating machine using the same.
  • a normal steam turbine generator is composed of a high-pressure turbine, a medium-pressure turbine, a low-pressure turbine, a generator rotor, and a plurality of rotating shafts connecting these. And the load which acts on these rotating shafts is supported by a journal bearing device or a radial bearing device, and can rotate efficiently.
  • a steam turbine uses high-temperature and high-pressure steam as a working fluid, and is configured to generate output while expanding the steam. Therefore, a thrust force (axial force) is generated on the rotating shaft due to the pressure difference between the steam inlet and outlet of each steam turbine.
  • a thrust force axial force
  • the pressure difference between the steam inlet and the steam outlet of each steam turbine is large, and the thrust force generated thereby becomes considerably large.
  • the bearing device is generally provided with a thrust bearing device in addition to a journal bearing device or a radial bearing device that supports the load of the rotating shaft, thereby responding to the thrust force generated in the axial direction.
  • the rotary machine means a gas turbine, a compressor, a supercharger (for example, a turbocharger for an automobile), a generator rotor, and the like in addition to a steam turbine.
  • Patent Document 1 A thrust bearing device used in such a rotating machine is described in Japanese Patent Laid-Open No. 52-67442 (Patent Document 1).
  • the thrust runner is a pair of bowl-shaped bearing members perpendicular to the rotation shaft and parallel to each other, formed by machining such as cutting or fitting on the rotation shaft. Is provided.
  • a base metal and thrust bearing plates attached to both sides of the base metal in the axial direction are arranged.
  • This base metal has an arcuate support portion on the outer peripheral side, and this support portion is placed on a support base provided with an arcuate receiving portion provided on a foundation on which the rotating machine is installed.
  • An oil supply path is provided in the base metal, and an oil film is formed between the thrust bearing plate and the thrust runner by supplying oil to the pair of thrust runner and the thrust bearing plate, and lubrication and cooling are performed.
  • the thrust bearing device disclosed in Patent Document 1 has the following problems. Before explaining the present invention, the configuration and problems of the thrust bearing device shown in Patent Document 1 will be explained.
  • the thrust bearing device shown in FIG. 7 shows a configuration when a thrust bearing device generally called a taper land type thrust bearing device is vertically sectioned.
  • reference numeral 10 denotes a rotating shaft of a rotating machine
  • thrust thrusters 11A and 11B which are a pair of bowl-shaped bearing members formed by machining such as cutting and fitting on a part of the rotating shaft 10. Is provided.
  • the thrust runners 11A and 11B are fixedly coupled to the rotary shaft 10.
  • a thrust bearing 12 is disposed between the thrust runner 11A and the thrust runner 11B, and the thrust bearing 12 restricts the movement of the thrust runner 11A and the thrust runner 11B. As a result, the axial direction of the rotary shaft 10 of the rotary machine Is restricted to a predetermined range.
  • the thrust bearing 12 includes a base metal 13 and thrust bearing plates 14A and 14B attached to both sides of the base metal 13, and the movement of the rotary shaft 10 is restricted by the thrust bearing plates 14A and 14B and the thrust runners 11A and 11B.
  • the outer peripheral portion of the base metal 13 has an arc-shaped support portion 13A in the axial direction, and this support portion 13A is placed on a support base 15 provided with an arc-shaped receiving portion 15A provided on the foundation on which the rotating machine is installed. Has been.
  • An oil supply passage 16 is provided inside the base metal 13, and a pair of thrust runners 11A and 11B and thrust bearing plates 14A and 14B are provided by two branched oil supply ports 16A and 16B opened to face the outer peripheral surface of the rotary shaft 10. By supplying oil to the thrust bearing plates 14A and 14B and the thrust runners 11A and 11B, an oil film is formed and lubrication and cooling are performed.
  • the gap Ga between the thrust runner 11B and the thrust bearing plate 14A is increased with respect to the gap Gb between the thrust runner 11B and the thrust bearing plate 14B.
  • the amount of oil sent between the thrust runner 11A and the thrust bearing plate 14A from the oil supply port 16A is larger than the amount of oil sent between the thrust runner 11B and the thrust bearing plate 14B from the oil supply port 16B. Phenomenon that increases.
  • the gap Ga between the thrust bearing plate 14A on the side not subjected to the thrust load and the thrust runner 11A is increased, so that the pressure at this portion is reduced, while the thrust bearing plate 14B and the thrust runner 11B on the side where the thrust load is applied. Since the gap Gb between the two is reduced, the pressure in this portion is increased, and as a result, the oil supplied from the oil supply passage 16 flows more toward the thrust bearing plate 14A and the thrust runner 11A.
  • An object of the present invention is to provide a thrust bearing device capable of appropriately maintaining the amount of oil supplied between a thrust bearing plate and a thrust runner provided in a thrust bearing device between a pair of thrust runners. There is.
  • a feature of the present invention is that the thrust bearing plate on the side where the thrust runner moves away when the rotating shaft moves in the axial direction is brought closer to the thrust thruster moving away, and the gap between the thrust runner and the thrust bearing plate is narrowed. is there.
  • the thrust bearing plate moves so as to narrow the gap between the thrust bearing plate and the thrust runner on the side where the thrust load is not applied.
  • An appropriate amount of oil can be supplied to the thrust bearing plate on the opposite side and the thrust runner side, a sufficient oil film is formed, and the amount of oil supplied from the oil supply passage can be reduced.
  • FIG. 2 is a longitudinal sectional view of a thrust bearing device for explaining a state when a thrust load is applied to the thrust bearing device shown in FIG. 1. It is a partially expanded sectional view of the thrust bearing device which becomes the other Example of this invention. It is the schematic block diagram which showed the rough structure of the electric power generating apparatus using a steam turbine as an example of the rotary machine to which this invention is applied. It is the longitudinal cross-sectional view which showed the longitudinal cross-section of the conventional thrust bearing apparatus.
  • FIG. 8 is a longitudinal sectional view of a conventional thrust bearing device for explaining a state when a thrust load is applied to the thrust bearing device shown in FIG. 7.
  • reference numeral 10 denotes a rotating shaft of a rotating machine, and a pair of bowl-shaped thrust runners 11 ⁇ / b> A and 11 ⁇ / b> B formed by machining such as cutting and fitting on a part of the rotating shaft 10. Is provided.
  • the thrust runners 11A and 11B are fixedly coupled to the rotary shaft 10.
  • a thrust bearing 12 is disposed between the thrust runner 11A and the thrust runner 11B, and the thrust bearing 12 restricts the movement of the thrust runner 11A and the thrust runner 11B. As a result, the axial direction of the rotary shaft 10 of the rotary machine Is restricted to a predetermined range.
  • the thrust bearing 12 includes a base metal 13 and thrust bearing plates 14A and 14B attached to both sides of the base metal 13, and the movement of the rotary shaft 10 is restricted by the thrust bearing plates 14A and 14B and the thrust runners 11A and 11B. .
  • the thrust bearing plates 14A and 14B have an annular shape having an inner peripheral portion and an outer peripheral portion facing each other with a gap around the rotating shaft 10, and the tapered portion 14C and A land portion 14D is formed.
  • the outer peripheral portion of the base metal 13 has an arcuate support portion 13A in the axial direction, and this support portion 13A is provided on the support stand 15 provided with an arcuate receiving portion 15A provided on the foundation on which the rotating machine is installed. It is placed.
  • An oil supply passage 16 is provided inside the base metal 13, and a pair of thrust runners 11A and 11B and thrust bearing plates 14A and 14B are provided by two branched oil supply ports 16A and 16B opened to face the outer peripheral surface of the rotary shaft 10.
  • An oil seal is provided between the rotary shaft 10 between the oil supply port 16A and the oil supply port 16B and the inner peripheral surface of the base metal 13, and the outer periphery of the rotary shaft 10 between the oil supply port 16A and the oil supply port 16B. The oil does not move.
  • the above is substantially the same configuration as the thrust bearing device shown in FIG.
  • the movable thrust bearing plates 14A and 14B described below have one feature.
  • annular grooves 17 ⁇ / b> A and 17 ⁇ / b> B are formed in the vicinity of the center of both side surfaces of the base metal 13 in the axial direction (the direction along the rotation axis 10) according to the shape of the base metal 13. Yes.
  • the groove portions 17A and 17B have a function of a receiving portion on one surface of the thrust bearing plates 14A and 14B.
  • the other surfaces of the thrust bearing plates 14A and 14B have a function of forming an oil film with the thrust runners 11A and 11B.
  • This oil film is formed by the action of the tapered portion 14C and the land portion 14D formed on the other surfaces of the thrust bearing plates 14A and 14B.
  • the formation of an oil film by the tapered portion 14C and the land portion 14D is well known as disclosed in Patent Document 1.
  • Inner circumferential annular projections 18A and 18B are formed on part of the side surfaces of the thrust bearing plates 14A and 14B facing the annular grooves 17A and 17B, respectively. 19B is formed, and these are accommodated in the grooves 17A and 17B.
  • the dimensions of the inner peripheral annular projections 18A and 18B are determined so as to slide in close contact with the inner peripheral sides of the groove portions 17A and 17B.
  • the dimensions of the outer peripheral annular projections 19A and 19B are determined so that they slide in close contact with the outer peripheral sides of the grooves 17A and 17B. Accordingly, the thrust bearing plates 14A and 14B are movable in the axial direction of the rotary shaft 10, and thereby adjust the lengths of the gaps Ga and Gb between the thrust bearing plates 14A and 14B and the thrust runners 11A and 11B. be able to.
  • the lengths of the inner annular projections 18A and 18B and the outer annular projections 19A and 19B are determined to be present in the grooves 17A and 17B even when the thrust bearing plates 11A and 11B are displaced to the maximum. ing. This prevents the oil supplied from the oil filler ports 16A and 16B from leaking through the groove portions 17A and 17B, thereby suppressing the oil pressure from rapidly decreasing.
  • Both are kept away from the bottom surfaces of the grooves 17A and 17B formed in the base metal 13 and the surfaces between the inner peripheral annular projections 18A and 18B and the outer peripheral annular projections 19A and 19B of the thrust bearing plates 14A and 14B.
  • An elastic body for example, a compression coil spring 20 is disposed.
  • the compression coil spring 20 is arranged in a precompressed state compressed in advance. As a result, since the base metal 13 is on the fixed side, the compression coil spring 20 urges the thrust bearing plates 14A and 14B with a force that brings the thrust bearing plates 14A and 14B closer to the thrust runners 11A and 11B.
  • the degree of preload of the compression coil spring 20 is determined from the relationship between the oil pressure supplied from the oil supply passage 16 between the thrust bearing plates 14A and 14B and the thrust runners 11A and 11B. That is, when the oil pressure between the thrust bearing plates 14A, 14B and the thrust runners 11A, 11B reaches a predetermined value or more, the force acting on the thrust bearing plates 14A, 14B reaches the pre-pressure of the compression coil spring 20, The thrust bearing plates 14A and 14B are moved toward the base metal 13 so that the gaps Ga and Gb between the thrust bearing plates 14A and 14B and the thrust runners 11A and 11B have a predetermined length.
  • the gaps Ga and Gb between the thrust bearing plates 14A and 14B and the thrust runners 11A and 11B are adjusted to substantially the same length. Will be.
  • the oil film be formed between the thrust bearing plates 14A and 14B and the thrust runners 11A and 11B.
  • the hydraulic pump is not required to be started in advance.
  • the gap Ga between the thrust runner 11A and the thrust bearing plate 14A becomes larger than the gap Gb between the thrust runner 11B and the thrust bearing plate 14B at this time, and the thrust runner 11B and the thrust from the oil supply port 16B.
  • a phenomenon has occurred in which the amount of oil sent between the thrust runner 11A and the thrust bearing plate 14A from the oil supply port 16A increases with respect to the amount of oil sent between the bearing plates 14B.
  • the thrust bearing plate 11A is movable. Therefore, when the pressure between the thrust bearing plate 14A and the thrust runner 11A becomes low, the thrust bearing plate is driven by the urging force of the compression coil spring 20. 14A moves to the right side in the drawing. That is, the thrust bearing plate 14A can move to a position where the urging force by the compression coil spring 20 and the oil pressure between the thrust bearing plate 14A and the thrust runner 11A are balanced.
  • the length of the gap Ga between the thrust bearing plate 14A and the thrust runner 11A is shorter than that of the conventional thrust bearing device, and the amount of oil passing through this portion is reduced.
  • the amount of oil sent to the thrust bearing plate 14B and the thrust runner 11B is increased by this amount as compared with the conventional thrust bearing device, and a sufficient amount of oil is ensured between the thrust bearing plate 14B and the thrust runner 11B. be able to.
  • a sufficient oil film can be secured between the thrust bearing plate 14B on the side where the thrust load is applied and the thrust runner 11B, and the thrust bearing plate 14A and the thrust side on which the thrust load is not applied. Wasted oil is not supplied between the runners 11A.
  • annular grooves 17A and 178B are formed on both side surfaces of the base metal 13, but annular grooves are formed on the thrust bearing plates 14A and 14B, and the thrust bearing plates 14A and 14B are formed.
  • the inner ring-shaped protrusions 18A and 18B and the outer ring-shaped protrusions 19A and 19B that are formed are formed on both side surfaces of the base metal 13, and the compression coil spring 20 is disposed between them. The effect obtained can be the same.
  • annular grooves 17 ⁇ / b> A and 17 ⁇ / b> B are formed in the vicinity of the center of both side surfaces in the axial direction of the base metal 13 in accordance with the shape of the base metal 13. Further, inner circumferential side annular projections 18A and 18B are formed on the surfaces of the thrust bearing plates 14A and 14B on the side facing the annular grooves 17A and 17B, and similarly, the outer circumferential side annular projections 19A and 19B are formed. Is formed.
  • annular inner intermediate ring 21 is also provided on the outer peripheral surfaces of the inner peripheral annular projections 18A and 18B and the inner peripheral surfaces of the grooves 17A and 17B.
  • annular outer intermediate ring 22 is also provided on the outer circumferential surface of the outer circumferential annular projections 19A and 19B and the outer circumferential surface of the grooves 17A and 17B.
  • Both the inner intermediate ring 21 and the outer intermediate ring 22 are fixed to the inner and outer peripheral surfaces of the grooves 17A and 17B by an adhesive or fixing bolts, and are configured not to move while the rotary machine is operating. Yes.
  • the inner intermediate ring 21 and the outer intermediate ring 22 are made of a low-friction material.
  • the inner intermediate ring 21 and the outer intermediate ring 22 are made of a chemically stable material containing polytetrafluoroethylene (PTFE). It is configured in an annular shape.
  • PTFE polytetrafluoroethylene
  • the sliding motion of the inner peripheral annular projections 18A and 18B and the outer peripheral annular projections 19A and 19B of the thrust bearing plates 14A and 14B is smooth.
  • the length of the gap Ga between the thrust runner 11A and the thrust bearing plate 14A and the length of the gap Gb between the thrust runner 11B and the thrust bearing plate 14A are managed under predetermined conditions. Has been.
  • the thrust runners 11A and 11B are closest to the thrust bearing plates 14A and 14B, that is, the rotary shaft 10 moves toward one side, and is formed by the thrust runner 11A and the thrust bearing plate 14A.
  • the total of the length of the gap Ga and the length of the gap Gb formed by the thrust runner 11 ⁇ / b> B and the thrust bearing plate 14 ⁇ / b> B is managed to be a predetermined ratio with respect to the shaft diameter of the rotary shaft 10. This ratio is determined by design, and this ratio is a movement amount that does not affect the performance of the rotating machine.
  • FIG. 6 shows a case where the present invention is applied to a steam turbine as a specific example of a rotating machine to which the thrust bearing device according to the present invention is applied.
  • a steam turbine generator is provided with a high-pressure turbine rotor 23, an intermediate-pressure turbine rotor 24, and a low-pressure turbine rotor 25.
  • These turbine rotor and generator rotor 26 are connected by a rotary shaft 28. It is connected.
  • the rotary shaft 28 is supported by disposing journal bearing devices or radial bearing devices 27 at both ends of the turbine rotors 23, 24, 25 and the generator rotor 26.
  • the thrust bearing device 12 according to the present invention is disposed at any position between the turbine rotors 23, 24, and 25 excluding the generator rotor 26.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Sliding-Contact Bearings (AREA)
  • Support Of The Bearing (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Supercharger (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
PCT/JP2012/073030 2012-09-10 2012-09-10 Dispositif de palier de butée et machine tournante utilisant celui-ci Ceased WO2014038080A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/JP2012/073030 WO2014038080A1 (fr) 2012-09-10 2012-09-10 Dispositif de palier de butée et machine tournante utilisant celui-ci
JP2014534136A JPWO2014038080A1 (ja) 2012-09-10 2012-09-10 スラスト軸受装置及びそれを用いた回転機械

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2012/073030 WO2014038080A1 (fr) 2012-09-10 2012-09-10 Dispositif de palier de butée et machine tournante utilisant celui-ci

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WO2014038080A1 true WO2014038080A1 (fr) 2014-03-13

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WO (1) WO2014038080A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106015032A (zh) * 2016-06-28 2016-10-12 杭州万辰机电科技有限公司 离心压缩机
CN106089999A (zh) * 2016-08-01 2016-11-09 吕伟涛 自动复位关节结构
WO2018041949A1 (fr) * 2016-09-02 2018-03-08 Danfoss Silicon Power Gmbh Arrangement de palier axial pour un arbre d'entraînement d'un compresseur centrifuge
CN107882767A (zh) * 2017-12-11 2018-04-06 重庆通用工业(集团)有限责任公司 压缩机轴承及压缩机
WO2018092781A1 (fr) * 2016-11-21 2018-05-24 株式会社Ihi Structure de palier et surcompresseur
WO2018129277A1 (fr) * 2017-01-09 2018-07-12 Borgwarner Inc. Turbocompresseur ayant un palier de butée avec écoulement d'huile polarisé
JP2019218878A (ja) * 2018-06-18 2019-12-26 三菱日立パワーシステムズ株式会社 蒸気タービン設備及びコンバインドサイクルプラント
WO2020166318A1 (fr) * 2019-02-14 2020-08-20 三菱重工マリンマシナリ株式会社 Structure de palier, compresseur d'alimentation comportant celle-ci, et procédé d'assemblage pour compresseur d'alimentation

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5267442A (en) * 1975-12-01 1977-06-03 Hitachi Ltd Taper land thrust bearing
JPS62204014U (fr) * 1986-06-19 1987-12-26
JP2002310142A (ja) * 2001-04-17 2002-10-23 Mitsubishi Heavy Ind Ltd スラスト軸受装置
JP2005155894A (ja) * 2003-10-31 2005-06-16 Toyota Central Res & Dev Lab Inc 流体軸受
JP2006112612A (ja) * 2004-09-15 2006-04-27 Mitsubishi Heavy Ind Ltd 軸受装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5267442A (en) * 1975-12-01 1977-06-03 Hitachi Ltd Taper land thrust bearing
JPS62204014U (fr) * 1986-06-19 1987-12-26
JP2002310142A (ja) * 2001-04-17 2002-10-23 Mitsubishi Heavy Ind Ltd スラスト軸受装置
JP2005155894A (ja) * 2003-10-31 2005-06-16 Toyota Central Res & Dev Lab Inc 流体軸受
JP2006112612A (ja) * 2004-09-15 2006-04-27 Mitsubishi Heavy Ind Ltd 軸受装置

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106015032A (zh) * 2016-06-28 2016-10-12 杭州万辰机电科技有限公司 离心压缩机
CN106089999A (zh) * 2016-08-01 2016-11-09 吕伟涛 自动复位关节结构
CN109790868A (zh) * 2016-09-02 2019-05-21 丹佛斯硅动力有限责任公司 用于离心式压缩机的驱动轴的轴向轴承装置
WO2018041949A1 (fr) * 2016-09-02 2018-03-08 Danfoss Silicon Power Gmbh Arrangement de palier axial pour un arbre d'entraînement d'un compresseur centrifuge
FR3055678A1 (fr) * 2016-09-02 2018-03-09 Danfoss Silicon Power Gmbh Agencement de palier axial pour un arbre d'entrainement d'un compresseur centrifuge
US10760583B2 (en) 2016-09-02 2020-09-01 Danfoss A/S Axial bearing arrangement for a drive shaft of a centrifugal compressor
JPWO2018092781A1 (ja) * 2016-11-21 2019-06-27 株式会社Ihi 軸受構造および過給機
CN109923292A (zh) * 2016-11-21 2019-06-21 株式会社Ihi 轴承构造及增压器
WO2018092781A1 (fr) * 2016-11-21 2018-05-24 株式会社Ihi Structure de palier et surcompresseur
US10865833B2 (en) 2016-11-21 2020-12-15 Ihi Corporation Bearing structure and turbocharger
WO2018129277A1 (fr) * 2017-01-09 2018-07-12 Borgwarner Inc. Turbocompresseur ayant un palier de butée avec écoulement d'huile polarisé
US10590946B2 (en) 2017-01-09 2020-03-17 Borgwarner Inc. Turbocharger having thrust bearing with biased oil flow
CN107882767A (zh) * 2017-12-11 2018-04-06 重庆通用工业(集团)有限责任公司 压缩机轴承及压缩机
CN107882767B (zh) * 2017-12-11 2024-01-12 重庆通用工业(集团)有限责任公司 压缩机轴承及压缩机
JP2019218878A (ja) * 2018-06-18 2019-12-26 三菱日立パワーシステムズ株式会社 蒸気タービン設備及びコンバインドサイクルプラント
CN112041543A (zh) * 2018-06-18 2020-12-04 三菱动力株式会社 蒸汽涡轮设备及联合循环设备
US11359520B2 (en) 2018-06-18 2022-06-14 Mitsubishi Power, Ltd. Steam turbine facility and combined cycle plant
JP7093238B2 (ja) 2018-06-18 2022-06-29 三菱重工業株式会社 蒸気タービン設備及びコンバインドサイクルプラント
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