WO2011018313A1

WO2011018313A1 - Anti-friction bearing

Info

Publication number: WO2011018313A1
Application number: PCT/EP2010/060524
Authority: WO
Inventors: Norbert Radinger; Tomas Smetana
Original assignee: Schaeffler Technologies Gmbh & Co. Kg
Priority date: 2009-08-14
Filing date: 2010-07-21
Publication date: 2011-02-17
Also published as: CN102575709A; EP2464881A1; DE102009037573A1

Abstract

The invention relates to an anti-friction bearing (1, 28) which has at least one first row (2) of rolling bodies (3) and at least one second row (4) of rolling bodies (3), an intermediate ring (5) for both rows (3, 4), an inner bearing ring (7, 29) for the first row (2) and an outer bearing ring (6) for the second row (4).

Description

Name of the invention

Rolling bearing description

Field of the invention

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.

In powertrains with double clutch bearings are often used with relatively large diameters and high rated speeds. In addition, due to their proximity to the combustion engine and clutch, these bearings are subject to additional stresses due to dust from the wear of the clutch and high temperatures.

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.

Description of the invention

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.

This object is achieved with the subject matter of claim 1 and that of a further independent claim.

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.

It is also conceivable that 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 Innenumfänge. 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. In radial rolling bearings, 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.

Preferably, the application of the inventions is provided in angular contact ball bearings. 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. In the annular gaps sit one or more of the respective rows. According to the invention, it is provided that both annular gaps are sealed together at least on one side of the rows by means of only one sealing arrangement. Another independent claim provides that 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.

Instead of two sealing arrangements per side of the bearing, preferably 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.

Furthermore, 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 Lagehnneren 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.

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.

Furthermore, several disc-shaped or profiled with any cross section sealing rings made of sheet metal can be combined with each other to labyrinth seals. A further embodiment of the invention provides that one of the sealing elements is formed integrally with one of the bearing rings. Such 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. Preferably, 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.

As a support for the 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. Alternatively, however, 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.

DETAILED DESCRIPTION OF THE DRAWING Components having the same meaning are identified by the same reference numeral.

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. Furthermore, 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. Likewise, the inner bearing ring 7 is encompassed by the intermediate ring 5.

Between the inner bearing ring 7 and the intermediate ring 5, a first annular gap 1 l is formed. In the first annular gap 1 1, the rolling elements 3 of the first row are arranged and guided with a ball cage 19. Between the intermediate ring 5 and the outer bearing ring 6, a second annular gap 12 is formed. In the second annular gap 12, the second row 4 rolling elements 3 is held by means of a ball cage 20.

The 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.

In the seal assembly 13 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. For this purpose, 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. Between a cylindrical intake 6b and an outer cylindrical section of the inner neren bearing ring 7, a sealing gap 27 is formed to form a gap seal, so that the seal assembly 14 with only one through the sealing gap

27 sealed sealing zone seals both annular gaps 1 1 and 12 non-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. Furthermore, 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

28 arranged. 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.

Between the inner bearing ring 29 and the intermediate ring 5, a first annular gap 1 l is formed. In the first annular gap 1 1, the rolling elements 3 of the first row are arranged and guided with a ball cage 19. Between the intermediate ring 5 and the outer bearing ring 6, a second annular gap 12 is formed. In the second annular gap 12, 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.

In the sealing arrangement 30, 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. Between a cylindrical inlet 6b and an outer cylindrical portion of the inner bearing ring 29, a sealing gap 27 is formed to form a gap seal, so that the seal assembly 14 with only one sealing zone seals both annular gaps 1 1 and 12.

reference numeral

Rolling bearings 23 Sealing gap, first row Rolling elements 24 Sealing gap

Rolling elements 25 seal carrier second row rolling elements 26 sealing element

Intermediate ring 27 Dichtspalta end face of the intermediate ring 28 Rolling

Outer bearing ring 29 Inner bearing ring flange 30 Sealing arrangement b Indentation 31 Sealing element inner bearing ring 32 Cap

a flange 32a collar

outer race 32b hollow cylindrical seat inner race 33 sealing member 0 outer race 34 sealing zone

1 annular gap 35 centrifugal disc 2 annular gap 35a seat

3 seal assembly 35b section

4 sealing arrangement 36 sealing gap

5 seal carrier 37 inner race 6 sealing element

7 sealing washer

7a hollow cylindrical seat

7b cover

7c doubling

8 rotation axis

9 ball cage

0 ball cage

1 sealing gap

2 sealing element

Claims

claims

Rolling bearing (1, 28), the at least one first row (2) rolling elements (3) and at least second row (4) rolling elements (3), an intermediate ring (5) for both rows (3, 4), an inner bearing ring ( 7, 29) for the first row (2) and an outer bearing ring (6) for the second row (4), wherein - the intermediate ring (5) with an outer raceway (8) for the

Rolling body (3) of the first row (2) and with an inner raceway (37) for the rolling elements (3) of the second row (4) is provided, - the rolling elements (3) of the first row (2) in each case in contact

Contact with the inner bearing ring (7) and the rolling elements (3) of the second row (4) are each in touching contact with the outer bearing ring (6), the rings (6, 7) concentric with the axis of rotation (18) of the

Rolling bearing (1, 28) are arranged, between the inner bearing ring (7) and the intermediate ring (5), a first annular gap (1 1) is formed, in which the first row (2) rolling elements (3) is arranged between the intermediate ring ( 5) and the outer bearing ring (6) a second annular gap (12) is formed, in which the second row (4) rolling elements (3) is arranged, the annular gaps (1 1, 12) are sealed on both sides of the rolling elements (3), characterized in that both annular gaps (1 1, 12) at least on one side of the rows (2, 4) are sealed together by means of a sealing arrangement (13, 14, 30).

2. Rolling bearing according to claim 1, characterized in that the sealing arrangement (13, 14, 30) has only one axially outer sealing zone.

3. Rolling bearing according to claim 2, characterized in that the sealing zone is a sealing gap (23, 27, 34) of a gap seal.

4. Rolling arrangement according to claim 3, characterized in that the gap seal by an at least partially disc-shaped sealing element (16, 26) and by the sealing gap (23, 27) between see the sealing element (16, 26) and one of the bearing rings (5, 7) is formed.

5. Rolling bearing according to claim 1, characterized in that the sealing arrangement (13, 14, 30) by a first at least partially disc-shaped sealing element (16, 22, 26, 31, 33) is formed by one of the bearing rings (6, 7 ), which axially covers one of the annular gaps (12) and which seals the other annular gap (12) on at least one sealing zone with at least one further element (6, 7, 16, 22, 26, 31, 33) of the rolling bearing 81, 28). seals.

6. Rolling bearing according to claim 5, characterized in that the further element of the bearing rings (6, 7).

7. Rolling bearing according to claim 5, characterized in that the further element is a second at least partially disk-shaped sealing element (33) of the sealing arrangement (30), wherein between the first sealing element (31) and the second sealing element (33) at least one Seal zone (34) is formed.

8. Rolling bearing according to the preamble of claim 1, characterized in that a sealing arrangement (13, 14, 30) at least one at least partially disc-shaped sealing element formed (16, 26, 31), which extends from one of the bearing rings (6) and thereby initially one of the annular gaps (12) radially bridged, then further contactless to the intermediate ring (5) in the direction of the other bearing ring (7) is oriented.

9. Rolling bearing according to claim 8, characterized in that the sealing element (26) is formed integrally with a bearing ring (6).

10. Rolling bearing according to claim 8, characterized in that two gap seals by means of the sealing element (16) are formed, wherein a first gap seal by the sealing element (16) and a

Sealing gap (21) between the intermediate ring (5) and the sealing element (16) is formed and a second gap seal by the sealing element (16) and a sealing gap (23) between one of the bearing rings and the sealing element (16) are formed.