EP2464881A1 - Palier à roulement - Google Patents

Palier à roulement

Info

Publication number
EP2464881A1
EP2464881A1 EP10736675A EP10736675A EP2464881A1 EP 2464881 A1 EP2464881 A1 EP 2464881A1 EP 10736675 A EP10736675 A EP 10736675A EP 10736675 A EP10736675 A EP 10736675A EP 2464881 A1 EP2464881 A1 EP 2464881A1
Authority
EP
European Patent Office
Prior art keywords
sealing
bearing
row
rolling
ring
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Withdrawn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
EP10736675A
Other languages
German (de)
English (en)
Inventor
Norbert Radinger
Tomas Smetana
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and 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 AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP2464881A1 publication Critical patent/EP2464881A1/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Withdrawn legal-status Critical Current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
    • 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
    • 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
    • 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
    • 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
    • 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 rolling bearing having at least a first row of rolling elements and an 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 race 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 sealed on both sides of the rolling elements.
  • Background of the Invention Such a roller bearing is described in more detail in DE 103 24 259 A1.
  • 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 each other, 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 symmetrical portion.
  • the rings are arranged one inside the other so that they radially between the rolling elements between them 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. At high speeds and thus with increasing influence of centrifugal force and / or at higher temperatures due to the relatively low consistency, it is difficult to keep the grease in the rolling contact and in the rolling bearing. Therefore, specially designed cages and complex seals are often realized on such bearings, which also make the rolling bearing more expensive.
  • DE10314259A1 For each row, DE10314259A1 provides two sealing arrangements in clutch release bearings, which have gap seals on one side of the three-row bearing and sealing lip seals on the other side. Although lip seals seal well at the sealing zones, they generate friction due to the sliding sealing contact. In addition, the cost of gaskets, especially when used in non-cutting sheet metal angular contact ball bearings, can account for half of the total cost of the bearing.
  • the object of the invention is to provide a roller bearing, the sealing arrangement can be produced easily and inexpensively despite the high demands placed on them.
  • 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 is because a common intermediate ring arranged. 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 provided in each case with an outer raceway for the rolling elements of the first row and with an inner raceway 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 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 of the same or differing 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 is irrelevant how many first rows and second rows has the rolling bearing. However, all first rows of a bearing have the same TeN- circle and / or are of the same storage 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, the 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 supporting rolling elements of the rows have the same or different diameter to each other.
  • 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 mecanicumflinde.
  • These definitions of the tracks also allow the inner race (s) of a series in whole or in part to be described by outer circumferences that are larger than the inner circumferences that describe the outer race of one or more other ranks.
  • 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 meaning the bearing arrangements in which the pressure lines do not run radially relative 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 rolling 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 substantially crowned, hollow cylindrical or annular disc-shaped or any other basic shapes to be sealed.
  • both annular gaps are sealed together at least on one side of the rows by means of only one sealing arrangement.
  • a sealing arrangement has at least one at least partially disc-shaped sealing element, which extends from one of the bearing rings and thereby initially radially bridged one of the annular gaps, then further contact-oriented to the intermediate ring in the direction of the other bearing ring.
  • both sides are provided with only one sealing arrangement.
  • the sealing arrangement is formed from at least one and alternatively from two or more sealing elements, of which at least one of them is primarily radially aligned by a seal carrier in the direction of the intermediate ring, thereby completely covering the annular gap axially and then extending past the intermediate ring and the other Annular gap with seals.
  • the advantage of such arrangements is that compared to the rolling bearings of the prior art sealing arrangements and thus sealing elements are saved.
  • the rolling bearing is simple and inexpensive to produce.
  • the number of sealing zones can be reduced, so that the rolling bearing is better sealed.
  • An embodiment of the invention therefore provides that the seal assembly only an outer sealing zone having.
  • the axially outer sealing zone is a sealed interface between the Lühnneren of the bearing and its surroundings.
  • the sealing zone can be formed by a sliding seal or, as an embodiment of the invention, by a gap seal.
  • gap seals By using gap seals can be reduced on the one hand friction losses in the rolling bearing and on the other hand can be dispensed with the use of expensive elastic sealing lips.
  • the use of disc-shaped sealing elements is possible, which can be produced simply and inexpensively by punching, bending, embossing and drawing in sheet metal in almost any desired shape.
  • a particularly simple gap seal is formed, for example, by a sealing disk and by a sealing gap between the sealing disk and a corresponding inner or outer cylindrical surface of a bearing ring.
  • a further embodiment of the invention provides that one of the sealing elements is formed integrally with one of the bearing rings.
  • a sealing element is for example a radial flange, which is formed from a collar or from a perforated bottom of a cup-shaped and manufactured as a drawing bearing ring.
  • at least one sealing gap is formed between the flange and one of the bearing rings, so that it is entirely possible to dispense with separate sealing elements and the rolling bearing can be produced even more favorably.
  • sealing elements optionally the inner, the outer or the intermediate rings of the rolling bearing according to the invention are provided.
  • Sealing gaps are optionally formed between the sealing elements themselves or between sealing elements and one or more of the aforementioned bearing rings.
  • the sealing elements are integrally formed with the respective seal carrier or sit as separate components on this. Sealing elements are all components which form a seal together with at least one further element of the sealing arrangement.
  • 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 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 inner bearing ring 7 is a longitudinally sectioned cup-shaped component with a perforated bottom with a radially outwardly directed edge, which is also referred to as a flange 7a.
  • the outer bearing ring 6 is a cup-shaped member with a feeder 6b at the bottom and with a radially inwardly directed flange 6a between bearing ring and 6b feeder.
  • 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 second row 4 provided.
  • 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.
  • annular gaps 1 1 and 12 are sealed on the left with only one seal assembly 13 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 16 of the seal assembly 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 washer 17 covers the annular gap 12 axially completely off 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 sealing gap 23 is the only axially outer sealing zone of the seal assembly 13.
  • 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 seal assembly 13 is thus formed by a first at least partially disc-shaped sealing element 16 in the form of the sealing washer 17, 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 27 with at least one another element of the rolling bearing 1 in the form of the flange 7a seals.
  • the roller bearing 1 is further provided with the sealing arrangement 14, which has a sealing element 26 in the form of a disk-shaped flange 6a of the outer bearing ring 6 formed integrally with the seal carrier 15.
  • 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 section of the inner neren bearing ring 7, so that the seal assembly 14 with only one through the sealing gap
  • 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 rolling 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. 6
  • the rings 5, 6 and 29 are concentric with the axis of rotation 18 of the rolling bearing
  • the outer bearing ring 6 surrounds a portion of the hollow cylindrical intermediate ring 5 circumferentially. Likewise, the inner bearing ring 29 is encompassed by the intermediate ring 5.
  • a first annular gap 1 l 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.
  • the 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 cooperatively form at least the single axially outer sealing zone 34 of the sealing arrangement 30.
  • 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 separate to the outer bearing ring 6 and the inner bearing ring 29 seal 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 sealing arrangement 30 has a third gap seal, which passes through a hollow-cylindrical section 35b of the centrifugal disk 35, the inside of the intermediate ring 5 and through a radial sealing gap 24 is formed between the hollow cylindrical portion 35b and the inside of the intermediate ring.
  • the sealing arrangement 30 is accordingly 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 axially covers one of the annular gaps 12 and which engages the other annular gap 11 at at least one sealing zone 34 at least one further 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).
EP10736675A 2009-08-14 2010-07-21 Palier à roulement Withdrawn EP2464881A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009037573A DE102009037573A1 (de) 2009-08-14 2009-08-14 Wälzlager
PCT/EP2010/060524 WO2011018313A1 (fr) 2009-08-14 2010-07-21 Palier à roulement

Publications (1)

Publication Number Publication Date
EP2464881A1 true EP2464881A1 (fr) 2012-06-20

Family

ID=42938262

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10736675A Withdrawn EP2464881A1 (fr) 2009-08-14 2010-07-21 Palier à roulement

Country Status (4)

Country Link
EP (1) EP2464881A1 (fr)
CN (1) CN102575709A (fr)
DE (1) DE102009037573A1 (fr)
WO (1) WO2011018313A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9822814B2 (en) * 2013-10-17 2017-11-21 Aktiebolaget Skf Bearing for combined loads
CN104819208A (zh) * 2014-01-31 2015-08-05 郝继先 串列式自调超高速轴承
US11913497B2 (en) 2022-05-10 2024-02-27 Aktiebolaget Skf Radially-nested bearing assembly

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4045100A (en) * 1973-02-14 1977-08-30 Societe Nouvelle De Roulements Concentric antifriction bearing assembly
JPS55139524A (en) * 1979-04-19 1980-10-31 Nachi Fujikoshi Corp Clutch release bearing
DE19631437A1 (de) * 1996-08-03 1998-02-05 Schaeffler Waelzlager Kg Zweireihiges Lager
DE10314259A1 (de) 2003-03-29 2004-10-07 Ina-Schaeffler Kg Mehrreihiges Wälzlager, insbesondere Ausrücklager für Kupplungen
DE10324259B4 (de) 2003-05-28 2005-04-28 Provertha Connectors Cables & Steckverbinder und Transportschutzgehäuse
CN101169156A (zh) * 2007-11-27 2008-04-30 周东海 叠合式滚动轴承

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2011018313A1 *

Also Published As

Publication number Publication date
WO2011018313A1 (fr) 2011-02-17
DE102009037573A1 (de) 2011-02-17
CN102575709A (zh) 2012-07-11

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