WO2018024831A1 - Palier à glissement axial possédant des surfaces de glissement cunéiformes en gradins - Google Patents

Palier à glissement axial possédant des surfaces de glissement cunéiformes en gradins Download PDF

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Publication number
WO2018024831A1
WO2018024831A1 PCT/EP2017/069665 EP2017069665W WO2018024831A1 WO 2018024831 A1 WO2018024831 A1 WO 2018024831A1 EP 2017069665 W EP2017069665 W EP 2017069665W WO 2018024831 A1 WO2018024831 A1 WO 2018024831A1
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WO
WIPO (PCT)
Prior art keywords
sliding
gap
wedge
sliding direction
bearing
Prior art date
Application number
PCT/EP2017/069665
Other languages
German (de)
English (en)
Inventor
Thomas Meyer
Original Assignee
Siemens Aktiengesellschaft
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 Siemens Aktiengesellschaft filed Critical Siemens Aktiengesellschaft
Publication of WO2018024831A1 publication Critical patent/WO2018024831A1/fr

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
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/047—Sliding-contact bearings for exclusively rotary movement for axial load only with fixed wedges to generate hydrodynamic pressure
    • 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
    • F16C33/1075—Wedges, e.g. ramps or lobes, for generating pressure
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • 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
    • F16C17/26—Systems consisting of a plurality of 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
    • F16C2360/00—Engines or pumps
    • F16C2360/31—Wind motors
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H2057/085—Bearings for orbital gears

Definitions

  • Axial ⁇ sliding bearing with wedge and the locking surfaces are described for example in WO2011 / 154078A1 (Daimler AG) 15.12.2011, DE102010044098 (Robert Bosch GmbH) 24.05.2012 and DE102014222514A1 (Bosch Mahle Turbo Systems GmbH & Co. KG) 14.01.2016.
  • two WTG transmissions are braked back-to-back on a load test rig and operated or tested under nominal load in both directions.
  • DE102012000836A1 Robot Bosch GmbH
  • the Axialgleitlager has firmly incorporated wedge surfaces.
  • the wedge surfaces are Hautar ⁇ in a first sliding surface, which is a second sliding surface, preferably a plane mating surface, spaced from it by a lubricating gap opposite.
  • first sliding direction locking surfaces adjoin the wedge surfaces in each case.
  • the wedge surfaces are aligned so that in the first Sliding direction of the lubrication gap is narrowed.
  • the Axialgleit ⁇ bearing has at the opposite ends of the wedge surfaces of the locking surfaces each have a step gap.
  • the step gap is designed in a direction opposite to the first sliding direction of the second sliding direction, that the lubricating gap is narrowed.
  • the invention is based on the realization that it tung for a driven only over a relatively short operating time Gleitrich- v2 of an axial plain bearing is sufficient, a hydrody ⁇ namic carrying capacity of the thrust bearing in this sliding ⁇ direction v2 by a step gap to realize, for example by a radial Lubricating groove is designed as a step gap.
  • a hydrody ⁇ namic carrying capacity of the thrust bearing in this sliding ⁇ direction v2 by a step gap to realize, for example by a radial Lubricating groove is designed as a step gap.
  • the advantage of a stepped gap with respect to a full wedge surface is that it requires less space and thus the wedge area required in a direction opposite the main direction of operation forming sliding vi of the axial sliding bearing for the unrestricted hydrodynamic Tragfä ⁇ ability only minimally reduced.
  • the existing in conventional trained Axialgleitlagern for two opposite directions Gleitver ⁇ avoided by two wedge surfaces.
  • serial test run of a WKA gearbox in a gearbox usually takes only a few hours.
  • a step gap can be used for the second sliding direction v2 of the axial sliding bearing during the series trial run.
  • the step gap in the second direction of sliding towards the lubrication gap has at least one rising step.
  • the step gap is arranged in a space of a radial lubrication groove of the axial sliding bearing.
  • a further preferred embodiment of the invention is a gear, comprising a gear and an inventive Axialgleitlager, wherein the gear is mounted axially by means of Axialgleitla ⁇ gers.
  • the transmission is designed as a planetary gear and the gear as a planetary gear of the planetary gear removablebil ⁇ det.
  • a further preferred embodiment of the invention is a wind turbine, comprising a rotor which is coupled via a Ro ⁇ torwelle torque transmitting with a transmission which is connected to a generator.
  • the Ge ⁇ gearbox formed in accordance with one of the embodiments of the invention described above.
  • ⁇ rod 1 shows a section of a conventional axial sliding bearing for a sliding direction.
  • Figure 2 is a section of a conventional thrust bearing for two opposite directions of sliding.
  • FIG. 6 shows an embodiment of a transmission according to the invention designed as a planetary gearbox
  • Fig. 7 shows an embodiment of a wind turbine according to the invention in a sectional oblique view.
  • Fig. 1 shows a section through a conventional hydrodyna ⁇ premix axial sliding bearing for a single sliding direction 12 comprises axial thrust bearing two sliding surfaces 2, 4 with a between the sliding surfaces 2, 4, forming the lubricating gap 3.
  • a first sliding surface 2 with surface structures has wedge-shaped surfaces 6 and Locking surfaces 8, wherein a wedge surface 6 in the sliding direction 12 of the Axialgleitlagers immediately followed by a locking surface 8.
  • a second sliding surface 4, the so-called counter surface is formed as a flat surface without surface ⁇ structures.
  • a wedge surface 6 is set against the anti-tread surface 4 in such a way that in the sliding direction 12 a narrowing lubricating gap 3 results, whereas a detent surface 8 runs parallel to the mating surface 4.
  • a lubricating groove is arranged in each case 10 in which lubricant trans ⁇ can be ported to the lubrication gap.
  • the first sliding surface 2 moves in the sliding direction 12 relative to the second sliding surface 4.
  • a convergent lubricating gap 3 forms in the region of the wedge surface 6, the effect of which is the hydrodynamic bearing capacity of the axial sliding bearing.
  • the hydrody ⁇ namic pressure zone extends over both partial surfaces, ie wedge surface 6 and locking surface 8. This is indicated in Fig. 1 by the pressure distribution curve 14.
  • the height of the pressure distribution curve 14 above the sliding surface 2 indicates the height of the hydrodynamic pressure.
  • Fig. 2 shows a section through a conventional hydrodyna ⁇ premix axial sliding bearing for two opposite sliding directions 12, 12 ⁇ .
  • the axial slide bearing comprises two sliding surfaces 2, 4 with a between the sliding surfaces 2, 4, forming the lubricating gap 3.
  • a first sliding surface 2 with surfaces ⁇ structure has wedge-shaped surfaces 6, 6 ⁇ and latching surfaces 8, wherein a first wedge surface 6 in a first sliding direction 12 the Axialgleitlagers immediately a locking surface 8 and after the locking surface 8 immediately follows a second wedge surface 6.
  • a second sliding surface 4, the so-called mating ⁇ surface is formed as a flat surface without surface structures.
  • a first wedge surface 6 is set against the mating surface 4 so that in the first sliding direction 12, a narrowing lubricating gap 3 results, whereas a locking surface 8 extends parallel to the mating surface 4.
  • a second wedge surface 6 is set against the mating surface 4 so that in the first sliding direction 12, a widening lubricating gap 3 results.
  • first sliding direction 12 opposite second sliding direction 12 ⁇ forms a second wedge surface 6 a narrowing lubricating gap 3 whereas a first wedge surface 6 a widening lubricating gap 3 he ⁇ gives.
  • a lubricating groove 10 is arranged, wherein lubricant can be transported into the lubricating gap 3.
  • the first sliding surface 2 moves relative to the second sliding surface 4 in one of the two sliding directions 12, 12 ⁇ .
  • a convergent lubricating gap 3 forms in the region of the first wedge surface 6, the effect of which is the hydrodynamic bearing capacity of the axial sliding bearing.
  • the hydrodynamic pressure zone extends over both partial surfaces, ie, the first wedge surface 6 and the first wedge surface 6 8 in the first sliding direction 12 below catch surface This is shown in Fig. 2 angedeu ⁇ tet by the first pressure distribution curve 14.
  • the height of the pressure distribution curve 14 above the sliding surface 2 indicates the height of the hydrodynamic pressure.
  • the first sliding direction 12 opposite sliding direction 12 ⁇ forms in the region of the second wedge surface 6 ⁇ a convergent lubricating gap 3, the effect of which is the hydrodynamic load capacity of Axialgleitla- gers.
  • the hydrodynamic pressure zone extends over both partial surfaces, ie, the second wedge surface 6 ⁇ and the second wedge surface 6 ⁇ in the second sliding direction 12 ⁇ subsequent locking surface 8. This is indicated in Fig. 2 by the second pressure distribution curve 14 ⁇ .
  • Fig. 3 shows a section of an axial sliding bearing according to the invention.
  • the axial sliding bearing can be used for two opposite directions of sliding 12, 12 ⁇ .
  • the axial sliding bearing according to the invention is of the basic structure similar to the axial sliding bearing shown in Fig. 2 for two opposite
  • the wedge surface 6 is against the mating surface 4 is so ⁇ is that results in the first sliding direction 12, a narrowing lubricating gap 3, whereas the locking surface 8 extends parallel to the mating surface 4.
  • the step gap 16 is formed against the mating surface 4 so that in the first sliding direction 12, a step-widening lubricating gap 3 results.
  • first wedge surface 6 with a tapered lubrication gap each have a lubrication groove 10 is arranged, wherein the lubricant trans ⁇ can be ported to the lubrication gap.
  • the first sliding surface 2 moves relative to the second sliding surface 4 in one of the two sliding directions 12, 12 ⁇ .
  • a convergent lubricating gap 3 forms in the region of the first wedge surface 6, the effect of which is the hydrodynamic bearing capacity of the axial sliding bearing.
  • the hydrodynamic pressure zone extends over both part surfaces, ie the wedge surface 6 and the wedge surface 6 in the first slide ⁇ direction 12 below catch surface 8. This is indicated in Fig. 3 by the first pressure distribution curve 14. there indicates the height of the pressure distribution curve 14 on the Gleitflä ⁇ che 2, the height of the hydrodynamic pressure.
  • a convergent lubricating gap 3 is formed in the region of the step gap 16, the effect of which is the hydrodynamic bearing capacity of the axial sliding bearing.
  • the hydrodynamic pressure zone extends over both sectionflä ⁇ Chen, that is, the step gap 16 and the stepped slot 16 ⁇ in the second sliding direction 12 below catch surface 8. This is interpreted in Fig. 3 ⁇ by the second pressure distribution curve 14 at ⁇ .
  • the second pressure distribution curve 14 ⁇ shows that the hydrodynamic pressure formed by the step gap 16 is less than the hydrodynamic pressure formed by the wedge surface 6.
  • FIG. 4 shows three different embodiments b), c) and d) for the dimensioning of a réellenspalt- axial ⁇ sliding bearing in comparison to a wedge-surface thrust bearing a).
  • the figure above shows a section of the Axi ⁇ algleitlagers with the sliding surfaces 2, 4, a between the sliding surfaces 2, 4 arranged lubricating gap 3 and an applied over the upper sliding surface 4 pressure distribution curve 14.
  • the figure below shows a plan view of the lower sliding surface 2.
  • the values of a second dimensionless load index ⁇ are plotted against the upper sliding surface 4, which in the form of a
  • ⁇ ⁇ p> hi 2 / (nUB).
  • ⁇ p> axial force F / (L B), ie per segment.
  • the wedge surface thrust bearing a has a wedge surface of width B and length L, wherein the height of the lubricating gap at the wide location of the wedge is 2.25 hl.
  • the Viable ⁇ ness ⁇ is 0.07.
  • the stepped gap axial sliding bearing b) has an upper plane of width B and length 0.45 L and a lower plane of the
  • Width B and length 0.55 L which are separated by a step vonei ⁇ each other.
  • the lubrication gap between the lower level of the first sliding surface 2 and the Schwarzlaufflä ⁇ che 4 has a height of 1.7 hl.
  • the carrying capacity is ⁇
  • the Actuallynspalt- axial plain bearing c) has a C-shaped obe ⁇ re level of width B and length 0.4 L and a lower level of width B and length 0.6 L, which are separated by a C-shaped step.
  • the lubricating gap between the lower level of the first sliding surface 2 and the mating surface 4 has a height of 2 hl.
  • the carrying capacity ⁇ be ⁇ contributes 0.114.
  • the decist- axial plain bearing d) has a C-shaped obe ⁇ re level of width B and length 0.76 L and a lower Ebe ⁇ ne the width of 0.76 B and 0.76 L length, which by a C-shaped Stage are separated from each other.
  • the carrying capacity ⁇ is 0,123.
  • Fig. 5 is a view of a thrust bearing again, the ⁇ sen section III-III in Fig. 3 is shown.
  • a second ring 40 is rotatably disposed, which carries a plane mating surface 4.
  • the mating surface 4 is spaced a lubricating gap 3 of a first ring 20, which bears a sliding surface 2 of Fig. 3, ie with wedge ⁇ surface 6, catch surface 8 and step slit 16.
  • the first ring 20 relative to the shaft 18 arranged dormant, which pierces the first ring 20 without contact in a central ring opening of the first ring 20.
  • Fig. 6 shows an embodiment of a transmission according to the invention, which is designed as a planetary gear.
  • the transmission 50 includes a provided with a helical gear 34 planetary wheel 55, which by means of a sliding bearing ⁇ sleeve 33 on a fixed in a support flange 32 of a Planetenträ ⁇ gers pinion shaft 30 about a rotation axis 35 which sammenzier supply with a symmetry axis of the pinion shaft 30 rotatably is stored.
  • the planet gear meshes simultaneously with a ring gear, not shown, and a sun gear, not shown.
  • a second ring 40 In an annular region of the front end which directly surrounds the planetary gear axle 30 surface of the planet 55, a second ring 40 is fixed against rotation, the sliding surface is separated from an opposite sliding surface of a first ring 20 through a lubrication gap.
  • the first ring 20 is coaxially fixed to the second ring 40 on the support cheek 32 of the planet carrier by screwings 31 rotatably.
  • the planet 55 of the planetary gear ⁇ 50 is axially supported by means of the axial sliding bearing formed by the two rings 20, 40.
  • Fig. 7 shows an embodiment of an inventive
  • Wind turbine 70 in a sectional oblique view The wind turbine 70 includes a rotor 75 which is connected via a rotor shaft 54 to transmit torque with a Planetengetrie ⁇ be 50.
  • the rotor shaft 54 is received in a rotor bearing 58.
  • the planetary gear 50 in turn is coupled to a generator 76 for generating electricity.
  • the rotor bearing 58, the rotor shaft 54, the planetary gear 50 and the generator 76 belong to a drive train 60 of the wind turbine 70.
  • the planetary gear 50 at least one not shown planet carrier 52 is included, which includes an embodiment of the invention Axialgleitlagers.
  • at least one planetary gear 55 of the planetary gear is axially ge ⁇ superimposed. As a result, the planetary gear 50 can be operated in two directions of rotation.

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)

Abstract

L'invention concerne un palier à glissement axial possédant des surfaces cunéiformes fixes (6) et des surfaces d'encliquetage (8) se raccordant à celles-ci dans un premier sens de glissement (12). Les surfaces cunéiformes (6) sont orientées de façon à rétrécir un interstice de lubrification (3) dans le premier sens de glissement (12). Le palier à glissement axial comporte, à chacune des extrémités des surfaces d'encliquetage (8) qui sont opposées aux surfaces cunéiformes, un interstice en gradin (16) qui est conçu, dans un deuxième sens de glissement (12') opposé au premier sens de glissement (12), de façon à rétrécir l'interstice de lubrification (3).
PCT/EP2017/069665 2016-08-04 2017-08-03 Palier à glissement axial possédant des surfaces de glissement cunéiformes en gradins WO2018024831A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016214451 2016-08-04
DE102016214451.0 2016-08-04

Publications (1)

Publication Number Publication Date
WO2018024831A1 true WO2018024831A1 (fr) 2018-02-08

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WO (1) WO2018024831A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110332226A (zh) * 2019-06-28 2019-10-15 湖南行必达网联科技有限公司 一种滑动轴承

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2996340A (en) * 1956-06-26 1961-08-15 Macks Elmer Fred Fluid dynamic bearing and method of making same
US3272999A (en) * 1963-10-17 1966-09-13 Vincent K Smith Air bearings for dynamoelectric machine
US3918773A (en) * 1974-01-07 1975-11-11 Litton Systems Inc Magnetic field responsive hydrodynamic bearing
DE3140017A1 (de) * 1981-10-08 1983-04-28 Flender A F Gmbh Co Kg Axiale hydrodynamische gleitlagerung
EP1353082A1 (fr) * 2002-04-11 2003-10-15 Morgan Construction Company Palier lisse et ensemble de patin à pression
EP1387097A1 (fr) * 2001-03-27 2004-02-04 Nok Corporation Palier de butee
WO2011154078A1 (fr) 2010-06-11 2011-12-15 Daimler Ag Palier axial, turbocompresseur à gaz d'échappement doté d'un palier axial et procédé de fabrication d'un palier axial
DE102010044098A1 (de) 2010-11-18 2012-05-24 Robert Bosch Gmbh Turbolader sowie Verfahren zu dessen Herstellung
DE102012000836A1 (de) 2012-01-18 2013-07-18 Robert Bosch Gmbh Getriebeprüfstandeinrichtung für Getriebe, insbesondere für Windkraftanlagen, mit einem im Antriebsstrang integrierten Generator
US20150043846A1 (en) * 2013-08-07 2015-02-12 Trane International Inc. Thrust bearing for hvac compressor
EP2884122A1 (fr) * 2013-12-16 2015-06-17 Areva Wind GmbH Palier de butée, ensemble de transmission, engrenage et générateur éolien
DE102014222514A1 (de) 2014-07-10 2016-01-14 Bosch Mahle Turbo Systems Gmbh & Co. Kg Axiallager

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2996340A (en) * 1956-06-26 1961-08-15 Macks Elmer Fred Fluid dynamic bearing and method of making same
US3272999A (en) * 1963-10-17 1966-09-13 Vincent K Smith Air bearings for dynamoelectric machine
US3918773A (en) * 1974-01-07 1975-11-11 Litton Systems Inc Magnetic field responsive hydrodynamic bearing
DE3140017A1 (de) * 1981-10-08 1983-04-28 Flender A F Gmbh Co Kg Axiale hydrodynamische gleitlagerung
EP1387097A1 (fr) * 2001-03-27 2004-02-04 Nok Corporation Palier de butee
EP1353082A1 (fr) * 2002-04-11 2003-10-15 Morgan Construction Company Palier lisse et ensemble de patin à pression
WO2011154078A1 (fr) 2010-06-11 2011-12-15 Daimler Ag Palier axial, turbocompresseur à gaz d'échappement doté d'un palier axial et procédé de fabrication d'un palier axial
DE102010044098A1 (de) 2010-11-18 2012-05-24 Robert Bosch Gmbh Turbolader sowie Verfahren zu dessen Herstellung
DE102012000836A1 (de) 2012-01-18 2013-07-18 Robert Bosch Gmbh Getriebeprüfstandeinrichtung für Getriebe, insbesondere für Windkraftanlagen, mit einem im Antriebsstrang integrierten Generator
US20150043846A1 (en) * 2013-08-07 2015-02-12 Trane International Inc. Thrust bearing for hvac compressor
EP2884122A1 (fr) * 2013-12-16 2015-06-17 Areva Wind GmbH Palier de butée, ensemble de transmission, engrenage et générateur éolien
DE102014222514A1 (de) 2014-07-10 2016-01-14 Bosch Mahle Turbo Systems Gmbh & Co. Kg Axiallager

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
WITTEL ET AL.: "Roloff/Matek Maschinenelemente", 2011, VIEWEG + TEUBNER VERLAG WIESBADEN

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110332226A (zh) * 2019-06-28 2019-10-15 湖南行必达网联科技有限公司 一种滑动轴承

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