WO2011018315A1

WO2011018315A1 - Rolling contact bearing

Info

Publication number: WO2011018315A1
Application number: PCT/EP2010/060527
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: EP2464882A1; DE102009037572A1

Abstract

The invention relates to a rolling contact bearing (1, 28) which has at least a first row (2) of rolling bodies (3) and at least a second row (4) of rolling bodies (3), an intermediate ring (5) for the two rows (2, 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 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.

Background of the invention

Such a rolling bearing is described in DE 103 24 259 A1 closer. 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.

As already stated in DE103 14 259 A1, today's generations of clutches require release bearings with larger diameters and / or release bearings which enable higher rotational speeds. 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.

The friction within a rolling bearing depends, among other things, on the load, the temperatures, the speed and the viscosity of the lubricating grease. In the booklet "Wälzlagerpraxis" Brändlein, Eschmann et al., Published by Vereinigte Fachbuchverlage GmbH, issue 1995, the chapter "Friction, temperature and lubrication" on page 210 states: "The resistance which a rolling bearing opposes to its rotation settles from rolling friction, sliding friction and lubricant friction together. " It also states: "The significance of friction is that it determines the heat generated in the bearing and thus influences the temperature of the bearing parts and the lubricant." On page 213, the same chapter continues: "The lubricant friction in a rolling bearing settles from the internal friction of the lubricant at the contact points and the churning and flexing work occurring at excess lubricant and higher speeds, the total lubricant friction depends primarily on the quantity and toughness of the lubricant however, it increases significantly with increasing speed, depending on the oil viscosity or fat consistency. "

As a rule of thumb for grease-lubricated roller bearings therefore greases with lower consistency should be used in bearings with higher operating speeds. In addition, these greases are generally much more expensive than greases that can be used in lower speed bearings because of the demands placed on them. In addition, it is more difficult with increasing speeds and thus increasing influence of centrifugal force and / or at higher temperatures due to the relatively low consistency 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 engine and clutch, these bearings are subject to additional stresses due to dust from the wear of the clutch and high temperatures.

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.

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, 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.

It is also conceivable that 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 Innenumfänge. 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. 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.

Preferred is the application of the invention are provided in angular contact ball bearings. 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.

The 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. 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.

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

Components with the same meaning are provided with the same reference numerals.

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 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. 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 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.

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 disc 17 covers the annular gap 12 axially completely 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 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. Between a cylindrical intake 6b and an outer cylindrical portion of the inner bearing ring 7, 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 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. Furthermore, 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. 6 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. 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 1 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, 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. 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 a second row (4) rolling elements (3), an intermediate ring (5) for both rows (2, 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, 29) and the rolling elements (3) of the second row (4) each in touching contact with the outer bearing ring (6), - the rings concentric with the axis of rotation (18) of the rolling bearing (1, 28 ) are arranged, between the inner bearing ring (7, 29) 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)

(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) with at least one sealing arrangement (13, 14, 30) of at least one annular Sealing element are at least partially covered, at least one seal carrier (15, 25) carries the seal element (16, 22, 26, 31, 33) from which the seal element (16, 22, 26, 31, 33) moves in the direction of one of the rings (6, 7) at least oriented, characterized in that the seal carrier (15, 25) is at least one to the intermediate ring (5) separate component.

2. Rolling bearing according to claim 1, characterized in that the outer bearing ring (6) is a seal carrier (15, 25).

3. Rolling bearing according to claim 2, characterized in that at least a part of a sealing element (22, 26) is formed integrally with the outer bearing gerring (6).

4. Rolling bearing according to claim 2, characterized in that at least one sealing arrangement (13, 14, 30) at least one to the outer bearing ring (6) separate sealing element (16, 22, 31, 33) has up.

5. Rolling bearing according to claim 4, characterized in that the separate sealing element (22, 33) of the inner bearing ring (7, 29) is supported.

6. Rolling bearing according to claim 1, characterized in that the inner bearing ring (7, 29) is a seal carrier (25).

7. Rolling bearing according to claim 1 or 6, characterized in that at least part of a sealing element (22) of the sealing arrangement

(13) is formed integrally with the inner bearing ring (7).

8. Rolling bearing according to claim 6, characterized in that at least one sealing arrangement (13, 14, 30) at least one to the inner bearing ring (7, 29) separate sealing element (16, 26, 31, 33).

9. Rolling bearing according to claim 8, characterized in that the separate sealing element (16, 26, 31) is supported by the outer bearing ring (6).

10. Rolling bearing according to claim 1, characterized in that the sealing arrangement (13, 14, 30) at least one gap seal from the sealing element (16, 22, 31, 33) and a sealing gap (21, 23, 24, 27) between the Seal member (16, 22, 31, 33) and one of the bearing rings (6, 7, 29) forms.

1 1. Rolling bearing according to claim 12, characterized in that the gap seal is formed by two of the sealing elements (31, 33) and at least one between the sealing elements (16, 22, 31, 33) extending sealing gap (23, 34), wherein each of the Dichtungselemen- te (16, 22, 31, 33) by another seal carrier (15, 25) is worn.

12. Rolling bearing, 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 (2, 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 elements (3) of the first row (2) and with an inner

Running track (37) for the rolling elements (3) of the second row (4) is provided, the rolling bodies (3) of the first row (2) each in touching contact with the inner bearing ring (7, 29) and the rolling elements (3) of the second row (4) are each in touching contact with the outer bearing ring (6) Rings are concentric with the axis of rotation (18) of the rolling bearing (1, 28) are arranged, between the inner bearing ring (7, 29) 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 ,, each of Annular gaps (1 1, 12) with at least one sealing arrangement (13, 14, 30) from at least one annular sealing element (16, 22, 31, 33) is sealed, characterized in that the intermediate ring (5) without contact to sealing elements (16, 22, 31, 33), wherein between at least one of the sealing elements (16, 22, 31, 33) and the intermediate ring (5) an annular gap is formed.

13. Rolling bearing according to claim 12, characterized in that the

Annular gap is a sealing gap (21, 24) of a gap seal which at least by the sealing element (16, 22, 31, 33) and between the sealing element (16, 22, 31, 33) and one of the bearing rings (6, 7, 29 ) formed sealing gap (21, 24) is formed.

14. Rolling bearing according to claim 12, characterized in that the outer bearing ring (6) carries at least one of the sealing elements.

15. Rolling bearing according to claim 12, characterized in that the inner bearing ring (7, 29) carries at least one of the sealing elements (22, 33).

16. Rolling bearing according to claim 12, characterized in that the inner bearing ring (7, 29) and the outer bearing ring (6) each carry at least one sealing element (16, 22, 31, 33).

17. Rolling bearing according to claim 16, characterized in that at least one of the sealing elements (22) is formed integrally with one of the rings (7).

18. Rolling bearing according to claim 12, characterized in that the outer bearing ring (6) surrounds at least a cylindrical portion of the intermediate ring (5) circumferentially and thereby at least a cylindrical portion of the inner bearing ring (7, 29) of the intermediate ring (5) is embraced ,