WO2011018315A1 - Palier à roulement - Google Patents

Palier à roulement Download PDF

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Publication number
WO2011018315A1
WO2011018315A1 PCT/EP2010/060527 EP2010060527W WO2011018315A1 WO 2011018315 A1 WO2011018315 A1 WO 2011018315A1 EP 2010060527 W EP2010060527 W EP 2010060527W WO 2011018315 A1 WO2011018315 A1 WO 2011018315A1
Authority
WO
WIPO (PCT)
Prior art keywords
rolling
row
ring
sealing
bearing
Prior art date
Application number
PCT/EP2010/060527
Other languages
German (de)
English (en)
Inventor
Norbert Radinger
Tomas Smetana
Original Assignee
Schaeffler Technologies Gmbh & Co. 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 Technologies Gmbh & Co. Kg filed Critical Schaeffler Technologies Gmbh & Co. Kg
Priority to EP10737019A priority Critical patent/EP2464882A1/fr
Publication of WO2011018315A1 publication Critical patent/WO2011018315A1/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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/80—Labyrinth sealings
    • 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
    • F16C19/18—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 two or more rows of balls
    • F16C19/181—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 two or more rows 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
    • F16C19/55—Systems consisting of a plurality of bearings with rolling friction with intermediate floating or independently-driven rings rotating at reduced speed or with other differential 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/767—Sealings of ball or roller bearings integral with the race
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/43—Clutches, e.g. disengaging 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/08—Details or arrangements of sealings not provided for in group F16D3/84

Definitions

  • the invention relates to a roller bearing having at least a first row Wälzkör- by and at least second row rolling elements, an intermediate ring for both rows, an inner bearing ring for the first row and an outer bearing ring for the second row, wherein the intermediate ring with an outer Raceway for the rolling elements of the first row and with an inner raceway for the
  • Rolling element of the second row is provided, the rolling elements of the first row are each in touching contact with the inner bearing ring and the rolling elements of the second row in each case in touching contact with the outer bearing ring, the rings are arranged concentrically to the axis of rotation of the rolling bearing, between the inner bearing ring and the intermediate ring, a first annular gap is formed, in which the first row of rolling elements is arranged - between the intermediate ring and the outer bearing ring, a second annular gap is formed, in which the second row rolling elements is arranged, the annular gaps are at least partially covered with at least one sealing arrangement of at least one annular sealing element, at least one sealing carrier carries the sealing element, from which the sealing element at least orients in the direction of one of the rings.
  • the rolling bearing is an angular contact ball bearing having at least a first row of rolling elements in the form of balls and an at least second row of rolling elements in the form of balls.
  • the angular contact ball bearing can also be referred to as a three-ring bearing, since it has an intermediate ring for both rows, an inner bearing ring for the first row and an outer bearing ring for the second row.
  • the inner bearing ring has an inner raceway for the balls of the first row.
  • the outer race for the balls of the first row is formed on the common for both rows intermediate ring.
  • the intermediate ring also has the inner raceway for the balls of the second row.
  • the outer bearing ring is provided with the outer race for the balls of the second row.
  • the rings are arranged concentrically to the rotational axis of the rolling bearing and at least partially pushed axially into one another, so that the outer bearing ring engages around the intermediate ring and the intermediate ring the circumferential circumference of the inner bearing ring at least on a rotationally symmetric portion.
  • the rings are arranged in such a way that they radially see the rolling elements between see themselves and limit radial gaps in the radial direction, which are filled in part by the balls, their cage and by fat.
  • the annular gaps are sealed on both sides of the rolling elements with seals. Under sealing is also the non-contact sealing with gap seals as grinding sealing contact to understand the sealing zones. Sealing zones are the zones where mutually relatively movable elements of the rolling bearing seal the annular gaps axially outwards or inwards.
  • DE 103 14 259 A1 shows an example of a double-row angular contact ball bearing of the type in which the two rows have a common bearing ring and different pitch circles. From DE 103 14 259 A1 it is known that the total rotational speed of the balls of the rows can be substantially halved by using a common intermediate ring and thus the diameter-speed characteristic can also be substantially halved.
  • a criterion that determines the permissible limits of the application of such bearings is therefore the diameter-speed characteristic.
  • This characteristic value is also referred to as speed characteristic value in Schaeffler KG's catalog HR1 of January 2006 in the description of the technical basics in the chapter “Lubrication” and is the product of speed and pitch circle diameter and is also dependent on the bearing type
  • the selection of the grease depends on the load and the speed of rotation, which on the one hand is important for the service life of the grease and, on the other hand, for the life of the rolling bearing.
  • DE103 14 259A1 provides sealing arrangements in clutch release bearings, which have gap seals on one side of the three-row bearing and on the other side sealingly fitting lip seals. Although lip seals seal well at the sealing zones, they generate friction due to the sliding sealing contact. In addition, the costs of tions, in particular when used in non-cutting angular contact ball bearings made of sheet metal, make up half of the total costs of the rolling bearing. Description of the invention
  • the object of the invention is to provide a rolling bearing, the seal arrangement is easy despite the high demands made on these to the safer protection of the bearing against dirt and on the holding of low viscosity fats at high speeds and high temperatures in the camp can be produced inexpensively.
  • the rolling bearing may have as rolling elements balls and / or rollers with the same or different from row to row diameters. It can be formed two or more rows. Between adjacent rows, a common intermediate ring is arranged in each case. Under adjacent rows are to be understood those whose rolling elements are on pitch circles with the same diameter or whose pitch circles differ.
  • the invention accordingly applies to radial and / or axial roller bearings.
  • the intermediate ring is in any case provided with an outer race for the rolling elements of the first row and with an inner race for the rolling elements of the second row.
  • Under a common bearing ring is a one-piece or composed of any number of pieces component to understand at which roll at least two different from the pitch circle or type rows rolling elements, which is arranged as an intermediate ring between these rows, and therefore at half the speed of the total speed of the bearing rotates.
  • the rolling bearing also has at least one inner bearing ring (inner ring) or at least one outer bearing ring (outer ring). In cases where the rolling bearing has more than a first row or a second row, the inner bearing ring and / or the outer bearing ring may also be formed as intermediate rings. At these bearing rings corresponding inner and outer raceways are formed for the rolling elements of the rows.
  • inner bearing rings, intermediate ring and outer bearing rings have more than one identical or different in terms of execution inner and / or outer raceway.
  • the first rows differ from the second rows by the diameter of their pitch circles and / or by the type of bearing assembly. It does not matter how many first rows and second rows the rolling bearing has. However, all first rows of a bearing have the same pitch circle and / or are of the same bearing type. Accordingly, all second rows of a rolling bearing have the same pitch circles among each other and / or are of the same bearing type. It is also conceivable that the rolling bearing according to the invention has third, fourth and nth rows of rolling elements, which differ from the other rows by other pitch circles and / or bearing types. Thus, it is conceivable that in a bearing arrangement radial ball bearings are combined with angular contact ball bearings and or four-point bearings.
  • the invention applies to rolling bearings in which all bearing rolling elements of the rows to each other have the same or differing diameter.
  • Inner raceways are the raceways of a row that are closer to the axis of rotation than the outer raceway in the same row.
  • the contours of the inner raceways are described about the axis of rotation by outer circumferences and the contours of the outer raceways by mecanicumfnature.
  • These definitions of tracks also allow the inner race (s) of a series to be described in whole or in part by outer circumferences. which are larger than the inner circumferences, through which the outer race of one or more other rows are described.
  • the raceways are formed on components that are either the classic rolling bearing rings or directly on shafts, bolts, housings and hollow cylindrical components of any kind.
  • the bearing rings of the rolling bearing are arranged concentrically to the rotational axis of the rolling bearing axially adjacent and / or nested.
  • the outer bearing ring preferably surrounds at least a portion of the intermediate ring on the circumference. At the same time and or alternatively, a portion of the inner bearing ring is encompassed by the intermediate ring.
  • Angular contact bearings are to be understood as the bearing arrangements in which the pressure lines do not extend radially to the bearing center axis, as is the case with deep groove ball bearings, but obliquely to the latter.
  • the pressure line run between the contacts of the rolling elements on the inner raceway and the outer raceway.
  • the pressure line extends in an imaginary axially along the axis of rotation of the bearing extending through the rolling elements and raceways laid cutting plane.
  • the cutting plane passes through the contacts of the rolling elements with the inner raceway and the outer raceway.
  • the rings are arranged with radial or axial distance from each other so that between them each annular gaps are formed.
  • the annular gaps may have essentially crowned, hollow cylindrical or annular disk-shaped or any other basic shapes to be sealed. In the annular gaps sit one or more of the respective rows.
  • the annular gaps are at least partially covered with at least one sealing arrangement comprising at least one annular sealing element.
  • Covered means sealed-sealing with one or more sealing lips and / or sealed with labyrinth seals or gap seals.
  • the seals sit on one or more seal carriers.
  • the one or the other Carrier are inventively no intermediate rings, but to this separate components such as either inner bearing rings, outer bearing rings or components of the surrounding construction. Another independent claim provides that the intermediate ring is non-contact with sealing elements, wherein between at least one of the sealing elements and the common bearing ring, an annular gap is formed.
  • sealing elements are integrally formed with the respective seal carrier or sit as separate components on this. Sealing elements are all components which, together with at least one further element of the sealing arrangement, form a seal.
  • the sealing elements are lips which together with one or more sealing surfaces form a seal.
  • sealing elements are preferably sheet metal rings in the form of sealing plates, centrifugal discs and angle rings, which together with one or more sealing gaps form gap seals or labyrinth seals. Gap seals are preferred because they are non-contact and therefore produce no friction in the rolling bearing.
  • the advantage of the invention is that the speed of the intermediate ring is disturbed neither by drag torques nor by additional friction due to touching sealing contact. Drag moments occur on the bearing rings, which are also carriers of sealing elements, due to the inertia of the rotating entrained sealing elements. Furthermore, friction moments are avoided on the intermediate rings, which arise in the sealing zones between the sealing lips and the sealing surface when the sealing surfaces are formed on the intermediate rings, or when the intermediate rings wear sealing lips. The speed of the drag rings and / or friction moments free intermediate rings can be determined better. Thus, the diameter-speed characteristic can be calculated more accurately. In addition, the bearings can be mounted easier and thus produce more cost-effectively. Detailed description of the drawing
  • the rolling bearing 1 shows a rolling bearing 1 in the embodiment of an angular contact ball bearing in a longitudinal section along its axis of rotation 18.
  • the rolling bearing 1 has at least a first row 2 rolling elements 3 and a second row 4 rolling elements 3.
  • the rolling elements 3 are designed as balls.
  • the rolling bearing is provided with an intermediate ring 5 and has an inner bearing ring 7 for the first row 2 and an outer bearing ring 6 for the second row 4.
  • the intermediate ring is provided with an outer race 8 for the rolling elements 3 of the first row 2 and with an inner race 37 for the rolling elements 3 of the second row 4.
  • the rolling elements 3 of the first row 2 are each in contact with an inner race 9 in contact with the inner bearing ring 7 and the rolling elements 3 of the second row 4 each in touching contact with an outer race 10 on the outer bearing ring. 6
  • the rings 5, 6 and 7 are arranged concentrically to the axis of rotation of the rolling bearing 1.
  • the outer bearing ring 6 engages around the largely hollow cylindrical intermediate ring 5 on the circumference.
  • the inner bearing ring 7 is encompassed by the intermediate ring 5.
  • a first annular gap 1 l is formed between the inner bearing ring 7 and the intermediate ring 5.
  • the rolling elements 3 of the first row are arranged and guided with a ball cage 19.
  • a second annular gap 12 is formed between the intermediate ring 5 and the outer bearing ring 6, a second annular gap 12 is formed.
  • the second row 4 rolling elements 3 is held by means of a ball cage 20.
  • the annular gaps 1 1 and 12 are left with only one seal assembly 13 and sealed right with only one seal assembly 14 and at least partially filled with grease.
  • the outer bearing ring 6 is a seal carrier 15 and carries a sealing element 16 of the seal arrangement 13. Accordingly, the seal carrier 15 is a separate component to the intermediate ring 5.
  • the sealing element 16 is a sealing plate 17 made of sheet metal, which is formed from a hollow cylindrical seat 17a and a cover plate 17b. Hollow-cylindrical seat 17a and cover plate 17b merge into one another at a doubling 17c produced by cold forming. The doubling 17 c serves as an axial stop when the sealing element 16 is pressed into the outer bearing ring 6.
  • both annular gaps 1 1 and 12 are sealed by the sealing element 16 as far as possible.
  • the sealing element 16 forms two gap seals.
  • the sealing disc 17 covers the annular gap 12 axially completely and remains to the intermediate ring 5 without contact.
  • the largely aligned in the direction of the inner bearing ring 7 cover plate 17b is slightly cranked at the radial height and limited to form a first gap seal of the seal assembly 13 an axial sealing gap 21 between the cover plate 17b and the end face 5a of the intermediate ring fifth
  • the sealing arrangement 13 furthermore has a sealing element 22 which is separate from the outer bearing ring 6 and which is formed by a disc-shaped flange 7a of the inner bearing ring 7, which in this case is a seal carrier 25.
  • the sealing element 22 forms, with the sealing element 15 separate from the inner bearing ring 7, a second gap seal of the sealing arrangement 13, which is formed by the cover plate 17b, the flange 7a and by an axial sealing gap 23 between the cover plate 17b and the flange 7a.
  • the seal assembly 13 has a third gap seal, which is formed by the radially outwardly facing end face 7b of the flange 7a, the inside of the intermediate ring 5 and by a radial sealing gap 24.
  • the sealing arrangement 13 is accordingly formed by a first, at least partially disk-shaped sealing element 16 in the form of the sealing disk 17 which extends from the outer bearing ring 6 which axially covers one of the annular gaps 12 and which engages the other annular gap 11 at at least one sealing zone 27 at least one further element of the rolling bearing 1 in the form of the flange 7a seals.
  • the rolling bearing 1 is further provided with the seal assembly 14 having a seal member 26 in the form of a disk-shaped flange 6a integrally formed with the seal carrier 15a of the outer race 6.
  • the flange 6a is opposite the sealing washer 17 and covers the second annular gap 12 axially completely, without touching the intermediate ring 5.
  • a sealing gap 27 is formed between a cylindrical intake 6b and an outer cylindrical portion of the inner bearing ring 7, to form a gap seal, so that the seal assembly 14 with only one sealing zone seals both annular gaps 1 1 and 12 without contact.
  • FIG. 2 shows a roller bearing 28 in the form of an angular contact ball bearing in a longitudinal section along its axis of rotation 18.
  • the roller bearing 28 has at least one first row 2 rolling elements 3 and a second row 4 rolling elements 3.
  • the rolling elements 3 are designed as balls.
  • the roller bearing is provided with an intermediate ring 5 and has an inner bearing ring 29 for the first row 2 and an outer bearing ring 6 for the second row 4.
  • the intermediate ring 5 is provided with an outer race 8 for the rolling elements 3 of the first row 2 and with an inner race 37 for the rolling elements 3 of the second row 4.
  • the rolling elements 3 of the first row 2 are each in contact with an inner raceway 9 in contact with the inner bearing ring 29 and the rolling elements 3 of the second row 4 in contact with an outer raceway 10 on the outer bearing ring.
  • the rings 5, 6 and 29 are arranged concentrically to the axis of rotation 18 of the rolling bearing 28.
  • the outer bearing ring 6 surrounds a portion of the hollow cylindrical intermediate ring 5 circumferentially.
  • the inner bearing ring 29 is encompassed by the intermediate ring 5.
  • a first annular gap 1 1 is formed between the inner bearing ring 29 and the intermediate ring 5.
  • the rolling elements 3 of the first row are arranged and guided with a ball cage 19.
  • a second annular gap 12 is formed between the intermediate ring 5 and the outer bearing ring 6, a second annular gap 12 is formed.
  • the second row 4 rolling elements 3 is held by means of a ball cage 20.
  • annular gaps 1 1 and 12 are left sealed with only one seal assembly 30 and right with only one seal assembly 14 and at least partially filled with grease.
  • the outer bearing ring 6 is a seal carrier 15 and carries a sealing element 31 of the seal assembly 30. Accordingly, the seal carrier 15 is a separate component to the intermediate ring 5.
  • the sealing element 31 is a cap 32 made of plastic, which is snapped onto the outer bearing ring 6 with a hollow cylindrical seat 32b.
  • both annular gaps 11 and 12 are sealed together by a seal which has two sealing elements 31 and 33 which, cooperating with one another, form at least the sealing zone 34.
  • the cap 32 covers the annular gap 12 axially completely and remains to the intermediate ring 5 without contact and limited to form a first gap seal the seal assembly an axial sealing gap 21 between the cap 32 and the end face 5 a of the intermediate ring. 5
  • the seal assembly 30 further includes the to the outer bearing ring. 6 and the inner Lagerhng 29 separate sealing member 33 which is formed by a centrifugal disc 35 which sits on the formed as a seal carrier 25 inner bearing ring 29.
  • the sealing element 31 forms, with the sealing element 33 separate from the inner bearing ring 29, a gap seal of the sealing arrangement 30 which is formed by a cylindrical collar 32a of the cap 32, a cylindrical seat 35a and by a radial sealing gap 36 between the collar 32a and the seat 35a.
  • the seal assembly 30 has a third gap seal, which is formed by a hollow cylindrical portion 35b of the centrifugal disc 35, the inside of the intermediate ring 5 and by a radial sealing gap 24 between the hollow cylindrical portion 35b and the inside of the intermediate ring.
  • the seal assembly 30 is thus formed by a first at least partially disc-shaped sealing element 31 in the form of the cap 32, which extends from the outer bearing ring 6, which covers one of the annular gaps 12 axially and the other annular gap 1 1 at least one sealing zone 34 with at least one another element of the rolling bearing 1 in the form of the centrifugal disc 35 seals without contact.
  • the rolling bearing 1 is further provided with the seal assembly 14 having a seal member 26 in the form of a disk-shaped flange 6a integrally formed with the seal carrier 15a of the outer race 6.
  • the flange 6a is opposite to the cap 32 and covers the second annular gap 12 axially completely, without touching the intermediate ring 5.
  • a sealing gap 27 is formed between a cylindrical inlet 6b and an outer cylindrical portion of the inner bearing ring 29, to form a gap seal, so that the seal assembly 14 with only one sealing zone seals both annular gaps 1 1 and 12.
  • Rolling elements 25 seal carrier second row rolling elements 26 sealing element
  • outer race 32b hollow cylindrical seat inner race 33 sealing member 0 outer race 34 sealing zone

Landscapes

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

Abstract

L'invention concerne un palier à roulement (1, 28) qui comprend au moins une première rangée (2) de corps roulants (3) et au moins une deuxième rangée (4) de corps roulants (3), une bague intermédiaire (5) pour les deux rangées (2, 4), une bague de roulement intérieure (7, 29) pour la première rangée (2), ainsi qu'une bague de roulement extérieure (6) pour la deuxième rangée (4).
PCT/EP2010/060527 2009-08-14 2010-07-21 Palier à roulement WO2011018315A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP10737019A EP2464882A1 (fr) 2009-08-14 2010-07-21 Palier à roulement

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009037572A DE102009037572A1 (de) 2009-08-14 2009-08-14 Wälzlager
DE102009037572.4 2009-08-14

Publications (1)

Publication Number Publication Date
WO2011018315A1 true WO2011018315A1 (fr) 2011-02-17

Family

ID=42938440

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/060527 WO2011018315A1 (fr) 2009-08-14 2010-07-21 Palier à roulement

Country Status (3)

Country Link
EP (1) EP2464882A1 (fr)
DE (1) DE102009037572A1 (fr)
WO (1) WO2011018315A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102221047A (zh) * 2011-06-02 2011-10-19 赵忠 多套圈轴承用中间层套圈
CN102322478B (zh) * 2011-06-02 2015-09-30 赵忠 带变径中间层套圈的多套圈轴承
EP2739875B1 (fr) * 2011-08-05 2015-10-14 Schaeffler Technologies AG & Co. KG Système de débrayage

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10314259A1 (de) 2003-03-29 2004-10-07 Ina-Schaeffler Kg Mehrreihiges Wälzlager, insbesondere Ausrücklager für Kupplungen

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10324259B4 (de) 2003-05-28 2005-04-28 Provertha Connectors Cables & Steckverbinder und Transportschutzgehäuse

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10314259A1 (de) 2003-03-29 2004-10-07 Ina-Schaeffler Kg Mehrreihiges Wälzlager, insbesondere Ausrücklager für Kupplungen

Also Published As

Publication number Publication date
DE102009037572A1 (de) 2011-02-17
EP2464882A1 (fr) 2012-06-20

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