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WO2008116443A1 - Palier à roulement - Google Patents

Palier à roulement Download PDF

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Publication number
WO2008116443A1
WO2008116443A1 PCT/DE2008/000449 DE2008000449W WO2008116443A1 WO 2008116443 A1 WO2008116443 A1 WO 2008116443A1 DE 2008000449 W DE2008000449 W DE 2008000449W WO 2008116443 A1 WO2008116443 A1 WO 2008116443A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
ring
recess
rolling
elastic element
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/DE2008/000449
Other languages
German (de)
English (en)
Inventor
Arnd Heeg
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.)
IHO Holding GmbH and Co KG
Original Assignee
Schaeffler KG
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 Schaeffler KG filed Critical Schaeffler KG
Publication of WO2008116443A1 publication Critical patent/WO2008116443A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F16C25/08—Ball or roller bearings self-adjusting
    • F16C25/083—Ball or roller bearings self-adjusting with resilient means acting axially on a race ring to preload the bearing
    • 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
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
    • F16C27/066—Ball or roller 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
    • F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
    • F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
    • F16C19/543—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact in O-arrangement

Definitions

  • the invention relates to a rolling bearing with at least one bearing ring, rolling on the running surface rolling elements.
  • Rolling bearings are known in a variety of embodiments (see for example DE 4221 802 A1, DE 28 33 769 C2) and proven.
  • a roller bearing comprises a number of rolling elements, which may be formed, for example, as balls, cylindrical rollers, needle rollers, tapered rollers or barrel rollers.
  • the rolling elements allow a rotational relative movement by being mounted on an inner race, e.g. in the bearing inner ring, and an outer tread, e.g. in the bearing outer ring, unroll.
  • the rolling elements are usually fixed in a cage.
  • spring elements in the form of e.g. Wellfedern or star springs are provided.
  • the roller bearings are subjected to an axial pretensioning force, so that the rolling elements perform a correct rolling movement independently of the operating situation on the assigned running surfaces.
  • spring elements can by design only partially apply relatively low spring forces. As a result, it is not guaranteed in every operating situation that no slippage of the rolling elements occurs.
  • an object of the present invention is to provide a rolling bearing which is reliably protected against slippage of the rolling elements in the load-free state with minimal axial space requirement and is optimized with regard to the external sealing with simple means.
  • the rolling bearing according to the invention comprises at least one bearing ring (the inner or outer ring), which has a recess which has a lateral opening. Inserted into the recess is an elastic element which is so dimensioned and protrudes axially out of the opening in such a way that it exerts a defined axial preload force on the bearing ring of the correspondingly designed mounting in the installed state by compression.
  • the flow of power via the elastic element, the bearing ring, the rolling elements and other components such as a second storage up to a corresponding mechanical abutment.
  • the bearing is advantageously provided with an integral pretensioning device, which is supported and compressed depending on the specific installation position and thus produces the desired axial pretensioning force.
  • Another significant advantage of the invention is that by the placement of the elastic element in the bearing-side recess no - apart from a slight protrusion of the elastic element out of the recess - additional axial space is required.
  • the rolling bearing according to the invention is characterized by a very compact design and yet is reliably protected by the integrated biasing device against unwanted slippage in load-free operating condition.
  • the prestressed elastic element additionally exerts a sealing function depending on the installation situation.
  • the elastic element fulfills a dual function and provides an integral outer seal, which is realized without additional space and advantageously without additional processing of corresponding components, such as bearing caps or the like.
  • the recess can also in mass-produced bearings in one complementary manufacturing step can be produced with relatively little effort.
  • the elastic element is an O-ring.
  • O-rings are available as standard components in a variety of designs. O-rings have inherently outstanding sealing properties, which in the context of the present invention mate with the spring-force-generating properties provided according to the invention.
  • FIG. 2 shows two roller bearings according to the invention in a floating bearing
  • FIG. 3 shows a roller bearing according to the invention in a vertical-rotor construction
  • FIG. 4 shows an inventive rolling bearing in installation combination with an angular contact ball bearing
  • FIG. 5 shows two roller bearings according to the invention in the so-called O arrangement
  • FIG. 6 shows two roller bearings according to the invention in the so-called X arrangement
  • FIG. 7 shows by way of example the determination of the total pressing force of an O
  • FIG. 8 shows examples of the size of the pressing force of O-rings as a function of the ring cross-section and of the material for 10% and 20% cross-sectional compression.
  • FIG. 1 shows a schematic diagram of a fixed / loose bearing of an end 1 of a shaft 2.
  • the inner ring 5 of a rolling bearing (deep groove ball bearing) 6 according to the invention is slipped onto a shaft shoulder 4.
  • rolling elements 9 held in a bearing cage roll off in the form of bearing balls.
  • the outer ring 10 of the rolling bearing 6 is held axially displaceable by a suitable choice of fit in a bore 12 of a bearing housing 14.
  • the rolling elements 9 roll on the running surface 15 of the outer ring 10.
  • the shoulder-remote area 18 of the shaft end 1 is mounted in a manner known per se with a deep groove ball bearing designed as a fixed bearing 20 with an inner 21 and an outer bearing ring 22.
  • the outer bearing ring 22 is held axially fixed in the bore 12 of the bearing housing 14 with a snap ring.
  • the two bearing inner rings 5, 21 are fixed on the shaft axially on the shaft shoulder 4, an intermediate ring 23 and a screwed to the shaft end cover.
  • the outer ring 10 is provided with a circumferential recess 24, which may be produced for example by twisting off a standard outer ring. This has the advantage that the present invention can be readily implemented in standard components or standard rolling bearings.
  • the recess could - depending on the thickness of the bearing ring, in which it is to be introduced - are turned as Einstechnut, which can still form an axial web to the lateral surface 27 of the bearing ring 10.
  • the groove is dimensioned in its width so that it ends straight on the lateral surface 27. It thus forms the recess 24 formed in the form of a shoulder, which thus has an opening 30 towards the axial end face 29 of the roller bearing 6.
  • an elastic element 32 in the form of a circumferential ring preferably an O-ring used.
  • the O-ring holds with appropriate dimensioning due to its residual stress in the recess and advantageously forms with the other components of the rolling bearing 6 a structural unit.
  • the bearing housing 14 is closed by a fixed by not shown screws bearing cap 38.
  • the bearing cap exerts on the elastic element 32 a force acting in the axial direction A from.
  • the elastic element (O-ring cross-section) is dimensioned so that it has a cross-sectional compression in the assembled state, which is not more than 30% even under unfavorable operating conditions. Unfavorable operating conditions can then occur when due to relative thermal movements and changes in length of the shaft 2 with respect to the bearing housing 14, the proposed axial gap 40 between the end face 29 of the rolling bearing and the inside of the bearing cap 38 is minimized.
  • the cross-sectional compression of the elastic member 32 should not exceed 30% due to the geometric configuration of the groove.
  • An essential aspect of the invention is that the elastic member 32 as described above exerts an axial bias on the outer ring 10, starting from him, a power flow through the rolling elements 9, the inner ring 5, the intermediate ring 23, the inner ring 21 and again over the rolling elements extends to the outer ring 22, in which the element 32 fulfills a spring function.
  • the elastic member 32 in dual function also exerts an excellent sealing effect to the bearing cap 38 (sealing function). Both of these functions are realized without significant increase in the axial space requirement.
  • FIGS. 2 to 6 illustrate the versatility of the possible applications of the roller bearing according to the invention, which basically has the configuration described in detail in connection with FIG. 1 in the variant embodiments.
  • Figure 2 shows a schematic diagram of a floating bearing with two rolling bearings 6 (deep groove ball bearings) according to the invention, which are arranged mirror-symmetrically and are held with their respective outer ring 10 in the bore 12 of the bearing housing 14. Both outer rings 10 can move in the axial direction A and are mutually provided in the manner described above with an elastic element 32 which is inserted into the circumferential recess 24.
  • FIG. 3 shows the use of a roller bearing 6 according to the invention in a vertical-rotor construction shown in principle.
  • the axial forces are absorbed by an angular contact ball bearing 50.
  • the angular contact ball bearing is designed radially free by a circumferential radial gap 51, so that when radial relief designed as a deep groove ball bearing according to the invention rolling bearing 6 could get into the undesirable slip run.
  • a height h of, for example, also 2.25 mm see Figure 1
  • an O-ring is used as the elastic element 32.
  • the outer ring 10 undergoes an axial bias in the vertical direction V, which is generated via the screwed-housing cover 53 via the outer ring 54 of the angular contact ball bearing 50 on the elastic member 32.
  • V vertical direction
  • the respective inner ring 5, 55 and the associated outer ring 10, 54 which permits sufficient compression of the elastic element 32.
  • a gap 40 between the outer ring 10 and another bearing cap 58 is provided.
  • Figure 4 shows a schematic diagram of a one-sided axial load and separate load bearing by a rolling bearing 6 according to the invention and a conventional angular contact ball bearing 60, which is held radially free by an axial gap 61 with its outer ring 62.
  • a risk of slippage of the angular contact ball bearing with axial relief is the bearing in a centrifugal pump, which has a high axial load in operation, which is taken up by the angular contact ball bearing in operation.
  • switching off the centrifugal pump operating conditions may occur in which the angular contact ball bearings is relieved and thus exposed to a risk of slipping.
  • Figure 5 shows an arrangement with two rolling bearings 70 according to the invention, which are each designed as angular contact ball bearings with defined ring projection between the bearing inner ring and bearing outer ring.
  • At least one outer ring 71 has a recess 72, which is introduced as a circumferential groove in the wider side (on-board side) 73 and in principle the same manner as described above repeatedly receives an elastic element 74 in the form of an O-ring 75.
  • the two bearings 70 are with respect to their Installation position in the so-called O-arrangement mounted (wide outer ring sides 73 are mutually), the inner rings 77 are axially braced against each other on the shaft 78. In this arrangement, there is a risk of slipping in operating conditions with very low external loads.
  • Figure 6 shows a schematic diagram of an arrangement of two designed as angular contact ball bearings according to the invention in a so-called X-arrangement.
  • the bearings 70 correspond to the roller bearings described in FIG. 5, but in the installation situation according to FIG. 6, the respective broad sides (on-board sides) 73 of the angular contact ball bearings 70 are oriented outward.
  • the recesses 72 introduced there into the outer ring 71 are oriented such that their openings 76 face the bearing caps 84, 85, ie are oriented laterally outward.
  • the bearing covers 84, 85 due to their screw connection with the bearing housing 88 in cooperation with the defined gap 86, respectively exert inwardly directed biasing forces F 3 , F 4 on the elastic elements 74 and O-rings 75.
  • a shim 90 of defined thickness is inserted between the inner rings 89 of the two rolling bearings 70. This allows the necessary displacement of the outer ring to ensure a slip-free run even at high axial load. If there is only one Axiallastides, also a conventional rolling bearing can be used for the always loaded thrust bearing.
  • FIG. 7 shows the determination of the total compressive force of a commercially available O-ring based on FIG. 8.
  • an O-ring with an inner ring diameter of 134 mm and a ring cross-section of 3 mm, material NBR 72 has been used (in the example: Freudenberg Simrit KG, article designation O-ring NBR72Shore14452146).
  • the resulting total force as a function of the respective spring stiffness (applied linear profile) or pressing force is shown for different cross-sectional crimpings (indicated in% of the cross-sectional area or in mm).
  • FIG. 8 schematically shows the size of the pressing force in N / cm of O-rings as a function of the ring cross-section and of the material for 10% (solid line) and 20% (dashed line) cross-sectional compression (source: Freudenberg Simrit KG).
  • the rolling bearing according to the invention using standard bearings with simple mechanical processing - for example, a cheap turning for grooving the groove on the bearing ring face or the turning off a corresponding paragraph - can be produced.
  • Another advantage is that the bearings prepared in this way could also be used elsewhere without a spring-elastic element being inserted into the recess. It would be conceivable to use the recess, for example, for a snap ring, which then fixes the outer ring in the axial direction in a particularly space-saving manner.
  • the antifriction bearing according to the invention is distinguished by a reduced axial space requirement, in spite of its additional features that are outstanding over the prior art (avoidance of slippage and integrated sealing function).

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

Palier à roulement (6) qui comporte des bagues de roulement (5, 10) sur les chemins de roulement (7, 15) desquelles roulent des corps de roulement (9). L'objet de la présente invention est la mise au point d'un palier à roulement à encombrement axial réduit au minimum, protégé de manière fiable à l'état de fonctionnement sans charge contre le glissement des corps de roulement et à étanchéification extérieure optimisée, avec des moyens simples. A cet effet, la bague de roulement (5, 10) présente un évidement (24) à dimensions adaptées, qui comporte une ouverture latérale (30). Un élément élastique (32) logé dans l'évidement (24) présente des dimensions telles et fait saillie axialement hors de l'évidement de manière telle qu'il produit par compression à l'état monté une force de précontrainte axiale (F) sur une bague de roulement (10; 54) en coopération avec le palier-support et / ou la structure environnante.
PCT/DE2008/000449 2007-03-23 2008-03-14 Palier à roulement Ceased WO2008116443A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007014010.1 2007-03-23
DE102007014010A DE102007014010A1 (de) 2007-03-23 2007-03-23 Wälzlager

Publications (1)

Publication Number Publication Date
WO2008116443A1 true WO2008116443A1 (fr) 2008-10-02

Family

ID=39713113

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2008/000449 Ceased WO2008116443A1 (fr) 2007-03-23 2008-03-14 Palier à roulement

Country Status (2)

Country Link
DE (1) DE102007014010A1 (fr)
WO (1) WO2008116443A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013222050A1 (de) * 2013-10-30 2015-04-30 Aktiebolaget Skf Lageranordnung
DE102013222049A1 (de) * 2013-10-30 2015-04-30 Aktiebolaget Skf Lageranordnung
CN110513391A (zh) * 2019-08-29 2019-11-29 宁波市镇海银球轴承有限公司 有o形圈预紧的两面密封双外圈长轴双列球轴承

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009015827B4 (de) * 2009-04-01 2023-11-02 Ab Skf Lageranordnung zur drehbaren Lagerung eines Maschinenteils
IT1398116B1 (it) * 2009-06-25 2013-02-07 D D S R L Meccanismo di movimentazione ed impianto solare utilizzante tale meccanismo

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EP0274682A2 (fr) * 1987-01-10 1988-07-20 NADELLA-Wälzlager GmbH Rouleau de guidage
WO2006014934A1 (fr) * 2004-07-26 2006-02-09 The Timken Company Roulement à capacité de compensation thermique

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US2414335A (en) * 1945-01-19 1947-01-14 Jack & Heintz Prec Ind Inc Ball-bearing assembly
US2588636A (en) * 1949-06-28 1952-03-11 Crise Mfg Company Noiseless self-aligning ball bearing
DE1077008B (de) * 1957-08-16 1960-03-03 Schaeffler Ohg Industriewerk Spielein- und nachstellbares Waelzlager, insbesondere Nadellager
US4223963A (en) 1977-08-01 1980-09-23 Glodin Jury N Antifriction bearing, method of making same and antifriction material for performing this method
DE8533642U1 (de) * 1985-11-29 1986-01-16 SKF GmbH, 8720 Schweinfurt Anordnung zur Anstellung eines Wälzlagers
DE4221802A1 (de) 1992-07-03 1994-01-05 Kugelfischer G Schaefer & Co Wärmedehnungsausgleichsring
GB9623126D0 (en) * 1996-11-06 1997-01-08 Timken Co Bearing assembly
DE102004034701A1 (de) * 2004-07-17 2006-02-02 Zf Lenksysteme Gmbh Wälzlager
DE102005003987B4 (de) * 2005-01-28 2018-07-05 Schaeffler Technologies AG & Co. KG Spielfreies Radialkugellager
FR2891596A1 (fr) * 2005-10-03 2007-04-06 Timken France Soc Par Actions Roulement axial.

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EP0274682A2 (fr) * 1987-01-10 1988-07-20 NADELLA-Wälzlager GmbH Rouleau de guidage
WO2006014934A1 (fr) * 2004-07-26 2006-02-09 The Timken Company Roulement à capacité de compensation thermique

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013222050A1 (de) * 2013-10-30 2015-04-30 Aktiebolaget Skf Lageranordnung
DE102013222049A1 (de) * 2013-10-30 2015-04-30 Aktiebolaget Skf Lageranordnung
WO2015063165A1 (fr) 2013-10-30 2015-05-07 Aktiebolaget Skf Structure de palier
WO2015063166A1 (fr) 2013-10-30 2015-05-07 Aktiebolaget Skf Structure de palier
DE102013222050B4 (de) * 2013-10-30 2015-05-13 Aktiebolaget Skf Lageranordnung
DE102013222049B4 (de) * 2013-10-30 2015-05-13 Aktiebolaget Skf Lageranordnung
US9841057B2 (en) 2013-10-30 2017-12-12 Aktiebolaget Skf Bearing assembly
US9939023B2 (en) 2013-10-30 2018-04-10 Aktiebolaget Skf Bearing assembly having a roller bearing connected to a bearing support by affixing plates and a spring element disposed between an affixing plate and bearing support
CN110513391A (zh) * 2019-08-29 2019-11-29 宁波市镇海银球轴承有限公司 有o形圈预紧的两面密封双外圈长轴双列球轴承

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