EP2997273A1 - Palier lisse radial - Google Patents

Palier lisse radial

Info

Publication number
EP2997273A1
EP2997273A1 EP14727429.4A EP14727429A EP2997273A1 EP 2997273 A1 EP2997273 A1 EP 2997273A1 EP 14727429 A EP14727429 A EP 14727429A EP 2997273 A1 EP2997273 A1 EP 2997273A1
Authority
EP
European Patent Office
Prior art keywords
bearing
bearing housing
radial
pressure block
housing
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.)
Withdrawn
Application number
EP14727429.4A
Other languages
German (de)
English (en)
Inventor
Steffen KÄMMERER
Ralph Rudolph
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.)
Voith Patent GmbH
Original Assignee
Voith Patent GmbH
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 Voith Patent GmbH filed Critical Voith Patent GmbH
Publication of EP2997273A1 publication Critical patent/EP2997273A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/03—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings
    • 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
    • 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
    • F16C37/00—Cooling of bearings
    • 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
    • F16C43/00—Assembling bearings
    • F16C43/02—Assembling sliding-contact bearings

Definitions

  • the invention relates to a radial sliding bearing, in detail with the features of the preamble of claim 1.
  • the invention further relates to a method for mounting a radial sliding bearing with support of the tilting segments on the bearing connection environment.
  • the radial slide bearing comprises a bearing housing with a bearing bore oriented along a bearing axis and a plurality of tilting segments arranged circumferentially relative to the bearing housing for supporting a shaft, the individual tilting segments each having a radially outer bearing surface for supporting on a bearing surface on a bearing surface Bearing housing guided pressure block has. In this case, at least indirect support of tilting segments takes place on the bearing housing.
  • the invention therefore an object of the invention to further develop a radial slide bearing of the type mentioned that this is even better meet the requirements in applications with very high peripheral speeds is characterized by a rigid segment support, also allows a radial space-saving training and in terms of manufacturing technology easy and is inexpensive to install.
  • a radial sliding bearing having a bearing housing with a bearing bore aligned along a bearing axis and a plurality of movable relative to the bearing housing and spaced from the bearing axis circumferentially about this arranged Kippsegmenten for supporting a shaft, wherein the single tilting pad each have a radially outer bearing surface for support on a support surface at a in the Bearing housing guided pressure block is, according to the invention thereby characterized in that the individual pressure block is guided free of support on the bearing housing in the radial direction movable in a radially extending through the bearing housing through hole and secured by a rotation against rotation in the circumferential direction of the through hole and the radial outer side of the pressure block at least partially, preferably completely with the outer diameter of the bearing housing or a sleeve enclosing this lies on a common cylinder surface.
  • Bushings are particularly useful when, for example, the bearing housing is made of cast iron and is too soft for the application.
  • the bearing housing enclosing socket is, for example, an eccentric bushing.
  • the inventively embodied radial plain bearing allows a stiff support of the tilting segments by the direct introduction of force into the bearing connection environment and is therefore also suitable for the storage of waves that rotate at very high speeds.
  • the radial slide bearing according to the invention is structurally simple and easy to assemble.
  • the support of the bearing surface on the support surface can be done directly or with the interposition of other components.
  • a lubricating film between the bearing surface and the support surface may be formed during operation of the radial sliding bearing.
  • the individual pressure block has at least one guide region for guiding in the bearing housing and in installation position at the radially inner end region a support region for forming the support surface, wherein the guide region is designed such that a clearance fit is provided between the outer circumference and the passage opening and the guide region in the radial direction has an extension which is dimensioned such that the support area is free of a bearing on the inner circumference of the bearing housing.
  • the individual pressure block and / or the tilting segment is made of a material having a modulus of elasticity greater than 200 GPa, in particular greater than 250 GPa.
  • the materials used are preferably technical ceramics. These allow a high radial stiffness while maintaining good thermal conductivity.
  • Another advantage consists in the significantly lower coefficient of thermal expansion, which significantly reduce the risk of bearing clearance reductions due to temperature increases in transient operation.
  • the formation of the individual passage opening in the bearing housing is formed in cross-section circular or oval.
  • a lubricant and / or coolant supply system which has at least one annular groove extending over at least a partial area in the circumferential direction around the bearing housing, which is arranged offset in the direction of the bearing axis in the direction of the bearing center or off-center wherein the annular groove is connected at least one radial bore in the housing with a gap formed between the individual tilting segments and the inner circumference of the bearing housing.
  • the central annular groove design allows inclusion of the pressure blocks in their radially outer end region for this function.
  • the radial mobility of the pressure block within the passage opening and securing in the circumferential direction by means of a rotation which is a form-locking with clearance on the guide portion of the pressure block effective and guided by the wall of the bearing housing fuse element, in particular comprises threaded pin. Due to its arrangement, this can already be used as an assembly aid during assembly of the bearing.
  • Radial plain bearings having at least 3 to 7 tilting segments, advantageously 4 to 5 tilting segments, are preferably used in the high-performance region for supporting purposes.
  • a method for assembling a radial plain bearing according to one of claims 1 to 7 is characterized by the following method steps:
  • a bearing housing with a bearing axis aligned along a bearing bore and a plurality of radially in relation to the bearing axis extending from the inner periphery to the outer circumference through holes;
  • Circumferential direction is designed with respect to the passage opening with a clearance fit and an oversize relative to its extension in installation position in the longitudinal direction;
  • the method allows a high dimensional stability of the bearing, since the adjustment can be made directly on the position of the printing blocks during assembly.
  • the pressure block can be clamped by means of a securing element of an already provided in the installed state of the bearing positive rotation against the passage opening.
  • the annular groove for a lubricating and cooling system can be incorporated into the bearing housing and / or the pressure block.
  • FIG. 1 shows, in a simplified schematic representation, a perspective view of a radial sliding bearing 1 designed according to the invention.
  • This comprises a bearing housing 2 with a bearing bore 3 extending along a longitudinal axis.
  • the longitudinal axis simultaneously forms the bearing axis LA.
  • a coordinate system is applied to the bearing axis LA here by way of example.
  • the x-axis coincides with the bearing axis LA and describes the extent along this or the axial direction.
  • the y-direction describes the extension in the radial direction.
  • FIGS. 2 a and 2 b a section of a radial sliding bearing 1, as shown in FIG. 1, is shown in an axially simplified schematic representation in an axial section.
  • Figure 2a illustrates the arrangement of the components for supporting a shaft 1 1 under static stress.
  • FIG. 2 b illustrates, on the basis of a view according to FIG. 2 a, the radial sliding bearing 1 in a state with tilting of the tilting segment 5.
  • the bearing housing 2 may be formed by a cylindrical sleeve. Preferably, this consists of at least two half-shells 4.1 and 4.2.
  • the radial sliding bearing 1 further comprises a plurality of movable relative to the bearing housing 2 and spaced from the longitudinal axis LA in the circumferential direction about these adjacent arranged tilting segments 5.
  • the tilting pads 5 are used for storing a not shown in Figure 1, in the figures 2a, 2b with 1 designated wave about its axis.
  • these comprise in each case a radially inner support surface 6 and a radially outer bearing surface 7 with which the tilting segments 5 are supported at least indirectly on a connection component, in particular a support surface 8.
  • the support surface 8 is formed on a pressure block 9, which is movably guided in the bearing housing 2 in the radial direction and secured in this against rotation.
  • the pressure block 9 is designed and arranged such that, in the installation position of the radial plain bearing, it is free of direct support on the bearing housing 2 and terminates flush with the outer circumference 10 of the bearing housing 2 or a bush by the bearing housing 2 in the radial direction.
  • the support of the forces thus takes place directly via the pressure block 9 in the bearing connection environment, ie the radial outer side 23 of the pressure block 9 is at least partially, preferably completely with the outer diameter dA of the bearing housing 2 on a common cylinder surface.
  • the guide of the pressure block 9 in the bearing housing 2 takes place in radially arranged in this and through the wall thickness, that is from the inner periphery 22 to the outer periphery 10 extending through holes 12. These through holes 12 are aligned in the radial direction.
  • the displaceability of the pressure block 9 in the radial direction is guided by a clearance between the outer circumference 10 of the passage opening 12 Pressure block 9 and the inner circumference 22 of the through hole 12 realized. All you need is a simple clearance fit.
  • the pressure block 9 is characterized in terms of its execution by at least two areas, a first support portion 13 and a second guide portion 14.
  • the function of the support portion 13 is the formation of the support surface 8.
  • the function of the guide portion 14th exists in the guide function in the bearing housing 2.
  • support area 13 and guide portion 14 are formed accordingly.
  • the support area 13 is made larger than the guide area 14 with respect to a center axis of the pressure block 9, which coincides with the center axis of the passage opening 12 in the installation position.
  • the support surface 6 formed on the tilting segment 5 is convex. Accordingly, the support surface 8 is formed on the pressure block 9 concave in the circumferential direction around the shaft 1 1 viewed.
  • the concrete geometric design of the pressure block 9 can be done in various ways.
  • the passage opening 12 is circular or oval.
  • the execution of the guide portion 14 of the pressure block 9 is complementary to circular or oval cross-section.
  • the pressure block 9 is preferably designed symmetrically with respect to a plane which is characterized by the center axis of the pressure block 9 and a perpendicular to this in the installed position in the axial direction.
  • the support region 13 extends beyond the guide region 14 on both sides on the radially inner end region of the pressure block 9 in the installed position and is thus designed on both sides with a projection in the circumferential direction about the bearing axis LA. By analogy, this also applies to the extent in the axial direction.
  • FIG. 2 b illustrates the support in the event of loading on the basis of a view according to FIG. 2 a. Visible here is a slight tilting of the tilting segment. 5 and thus the support surface 6 relative to the outer circumference of the shaft 1 to be supported.
  • an anti-rotation lock 15 is provided.
  • the support region 13 is arranged at its side directed towards the guide region 14 at a distance from the inner circumference 22 of the bearing housing 2 and is thus free from direct support on the bearing housing 2.
  • an anti-rotation lock 15 is provided.
  • the anti-twist device 15 comprises fixing means in the form of threaded pins 16, which act on the outer circumference of the guide region 14 of the pressure block 9.
  • FIG. 3 a illustrates a detail of a view in an axial section plane. Recognizable are the bearing housing 2 in its axial direction of extent, the pressure block 9 after installation and the tilting segment 5, which is viewed in the radial direction in the axial and circumferential direction via a contact area on the support surface 8 of the pressure block 9 is supported.
  • the rotation lock 15 is thereby positioned starting from the side surfaces 17 and 18 of the bearing housing 2 perpendicular to these.
  • a threaded pin 16 in the bearing housing 2 starting from a side surface 17 in a direction of the through hole 12 extending and opening into this threaded hole 20 is performed.
  • the threaded bore 20 preferably extends orthogonally to the passage opening 12.
  • FIG. 3b shows the arrangement and design of the anti-twist device 15 in a section AA from FIG. 3a.
  • the rotation 15 is effective on the outer circumference of the guide portion 14 of the pressure block 9.
  • the threaded pin 16 of Anti-rotation 15 engages here in recesses on the outer circumference of the guide portion 14 and acts in particular during assembly with this frictionally under fixation of the pressure block 9 in its position within the passage opening 12 in the radial direction together.
  • FIG. 4 shows a perspective view of the arrangement of the individual components relative to one another and the fixing of the tilting segments 5 in the radial and circumferential direction with play via means 24 in the form of segment holding pins on the side windows 21 in a section from an axially perpendicular section through the radial sliding bearing 1.
  • the function of the segment holding pins is in storage and transport in a backup of Kippsegmente 5 from falling out and allowing mobility in the radial and tangential or circumferential direction within a permissible game.
  • the segment holding pins can either be firmly connected to the side windows and executed with play engaging in the tilting segments 5 or vice versa.
  • the individual connection can be made non-positive or positive.
  • FIGS. 1 to 4 illustrate a particularly advantageous embodiment of a radial sliding bearing 1 with a lubricant and coolant supply system 25 associated therewith and not shown here in detail, which comprises an annular groove 19 arranged on the outer circumference of the bearing housing 2 in the circumferential direction about the longitudinal axis.
  • the annular groove 19 is part of the coolant supply system.
  • the annular groove 19 is arranged centrally relative to the axial extent of the radial sliding bearing 1.
  • the annular groove 19 is arranged in the material of the bearing housing 2 and in the direction away from the shaft 1 1 and flush with the outer periphery 10 of the bearing housing 2 final radial outer side 23 of the pressure block 9.
  • the annular groove 19 is connected via at least one connecting bore with a radial direction component in the bearing housing 2 with a space between the individual tilting segments 5.
  • This connecting channel guides the lubricant into the region between the tilting segment 5 and the inner circumference 22 of the bearing housing 2 and the shaft surface 11.
  • the lubricant or coolant used for the radial sliding bearing 1 according to the invention is usually oil. However, it is also conceivable to use water or another mixture.
  • the function of the annular groove 19 is the oil supply of each, formed by a respective tilting segment 5 and the shaft to be supported 1 1 gap. Also conceivable are designs with grooves symmetrically to the bearing center on the outer diameter of the bearing housing 2 and thus outside of the pressure block 9.
  • supply rails 26 are provided for lubricants or coolant, with the annular groove 19 are connected via the connecting channels, in particular oil channels in a conductive connection.
  • the feed bars 26 and the oil passages are preferably inclined relative to a radial jet.
  • the longitudinal axis of the oil passages can, for example, in an axially perpendicular section through the bearing axis arranged in the manner of secants to the limited by the lateral surface of the shaft 1 1 circle.
  • the supply to the tilting segment 5 takes place on the side of the inlet edge 27. Under this edge of the tilting segment 5 is to be understood, which is first swept in the direction of rotation of the shaft 1 1 of the shaft 1 1.
  • each of the feed bars 26 has threaded holes for screwing dosing screws.
  • FIG. 5 shows an embodiment of the bearing housing 2.
  • the passage openings 12, which are arranged centrally in the axial section, are provided in a complementary number to the number of tilting segments 5 to be supported and are arranged equidistant from one another in the circumferential direction adjacent to one another.
  • FIG. 6 shows a pressure block 9 as suitable for the embodiment of the radial plain bearing 1 according to FIGS. 1 to 4.
  • FIGS. 7a to 7d illustrate, in a simplified schematic representation, the individual assembly steps of the manufacture of the radial plain bearing 1.
  • the bearing housing 2 is provided with the through openings 12 extending in the radial direction from the inner to the outer circumference, for receiving the pressure blocks 9.
  • FIG. 7a shows the bearing housing ring. This can be carried out in several parts as already stated.
  • FIG. 7b illustrates the provision of the pressure block 9 with at least two partial regions, the guide region 14 and the support region forming the support and support function and the support surface 8.
  • the pressure block 9 can be executed in the guide area 14 already with the incorporated portion of the annular groove 18.
  • the guide region 14 is also conceivable to carry out the guide region 14 as a full segment also in the area flush with the outer circumference of the bearing housing 2.
  • the individual tilting segments 5 are provided.
  • the positioning of the individual components of bearing housing 2, pressure block 9 and tilting segment 5 takes place relative to one another.
  • the individual pressure blocks 9 are introduced from the side of the inner circumference 22 of the bearing housing 2 into the passage opening 12 with the guide region 14.
  • the guide portion 14 of the pressure block 9 is executed with respect to its extension in the installed position as a prefabricated basic component with an oversize.
  • the positioning of the tilting segments 5 in their position defining the position takes place by positioning the tilting pad 5 relative to the respective Pressure block 9 and applying a pressure to the individual pressure block 9 and the tilting pad 5 against a centered in the bearing housing 2 adjusting bolts for setting the required tolerance.
  • the fixing takes place by means of the rotation, here the set screw 16, which biases the pressure block 9 relative to the passage opening 12 in the radial direction, ie the pressure blocks 9 with the tilting pads 5 are pressed against an adjusting bolt and held by clamping the rotation 15 in position.
  • FIG. 8 shows by way of example in a highly simplified representation such an embodiment in which the bearing housing 2, here by way of example consisting of two bearing housing shells, is surrounded by a support ring in the form of a bushing 29.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Sliding-Contact Bearings (AREA)
  • Support Of The Bearing (AREA)

Abstract

L'invention concerne un palier lisse radial qui comporte un logement de palier (2) avec un alésage de palier (3) orienté le long d'un axe de palier (LA) et plusieurs segments oscillants (5) montés mobiles autour de celui-ci par rapport au logement de palier (2) et à distance de l'axe de palier (LA) dans le sens de la circonférence afin de supporter un arbre (11), chaque segment oscillant (5) individuel comportant une surface de palier extérieure (7) destinée à l'appui contre une surface support (8) sur un bloc de pression (9) guidé dans le logement de palier (2). L'invention est caractérisée en ce qu'un bloc de pression (9) individuel est guidé de façon à se déplacer librement dans la direction radiale depuis un appui sur le logement de palier (2) jusque dans un orifice de passage (12) qui s'étend dans la direction radiale à travers le logement de palier (2), il est bloqué au moyen d'une sécurité antirotation (15) pour l'empêcher de tourner dans le sens de la circonférence de l'orifice de passage (12) et le coté extérieur radial du bloc de pression (9) se situe au moins partiellement, de préférence entièrement, avec le diamètre extérieur du logement de palier (2) ou d'une douille enserrant celui-ci sur une surface cylindrique commune.
EP14727429.4A 2013-05-17 2014-05-14 Palier lisse radial Withdrawn EP2997273A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013209193 2013-05-17
PCT/EP2014/059827 WO2014184232A1 (fr) 2013-05-17 2014-05-14 Palier lisse radial

Publications (1)

Publication Number Publication Date
EP2997273A1 true EP2997273A1 (fr) 2016-03-23

Family

ID=51831555

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14727429.4A Withdrawn EP2997273A1 (fr) 2013-05-17 2014-05-14 Palier lisse radial

Country Status (4)

Country Link
US (1) US20160069384A1 (fr)
EP (1) EP2997273A1 (fr)
DE (1) DE102014209062A1 (fr)
WO (1) WO2014184232A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3250834B1 (fr) * 2015-01-30 2021-01-20 Siemens Aktiengesellschaft Patin oscillant pour soutenir un tourillon de rotor dans un moteur à turbine
DE102016106005B4 (de) * 2016-04-01 2019-12-24 Zollern Bhw Gleitlager Gmbh & Co. Kg Kippsegmentlager
DE102019101974A1 (de) 2019-01-28 2020-07-30 Man Energy Solutions Se Gleitlager mit additiv gefertigten Strukturen

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Publication number Priority date Publication date Assignee Title
DE1525317A1 (de) * 1965-10-04 1969-07-31 Schleifmaschinenwerk Karl Marx Hydrodynamisches Lager
CH558481A (de) 1972-04-06 1975-01-31 Bbc Brown Boveri & Cie Gleitlager.
GB9400392D0 (en) 1994-01-11 1994-03-09 Chester Keith I Improved bearing assembly
JPH07293554A (ja) 1994-04-21 1995-11-07 Mitsubishi Heavy Ind Ltd ティルティングパッド型軸受装置
GB2292192B (en) 1994-08-06 1997-12-10 Glacier Metal Co Ltd Journal bearings
US5795076A (en) * 1995-10-13 1998-08-18 Orion Corporation Tilt pad hydrodynamic bearing for rotating machinery
US5738447A (en) 1997-04-01 1998-04-14 Rotating Machinery Technology, Inc. Pad bearing assembly with fluid spray and blocker bar
GB2358892B (en) 2000-02-05 2004-06-09 Federal Mogul Rpb Ltd Tilting pad bearing arrangement
US6485182B2 (en) 2001-03-28 2002-11-26 Rotating Machinery Technology, Inc. Sleeve bearing with bypass cooling
GB0115336D0 (en) * 2001-06-22 2001-08-15 Federal Mogul Rpb Ltd Bearing
RU2315211C2 (ru) 2003-06-07 2008-01-20 Сименс Акциенгезелльшафт Узел сегментного подшипника
GB2424043A (en) 2005-03-12 2006-09-13 Siemens Ind Turbomachinery Ltd A tilting pad bearing assembly
AT507397A1 (de) * 2008-09-29 2010-04-15 Miba Gleitlager Gmbh Nabenwellen-gleitlager
JP5094833B2 (ja) 2009-12-28 2012-12-12 株式会社日立製作所 ティルティングパッドジャーナル軸受装置

Non-Patent Citations (1)

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Title
See references of WO2014184232A1 *

Also Published As

Publication number Publication date
DE102014209062A1 (de) 2014-11-20
WO2014184232A1 (fr) 2014-11-20
US20160069384A1 (en) 2016-03-10

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