DE102016220392A1 - Ball Roller Bearings - Google Patents

Abstract

The invention relates to a ball roller bearing (10) with an inner ring (12) arranged concentrically with respect to a longitudinal center axis (16) and an outer ring (14) coaxially surrounding it, wherein a plurality of ball rollers (24, 26, 28, 30) whose geometry respectively a ball flattened on both sides symmetrically with mutually parallel plane surfaces (32, 34), in a first row (20) and a second row (22) are arranged, wherein the ball rollers (24, 26, 28, 30) in a first and a second, respectively comb-like sub-cage (40, 42) circumferentially equally spaced apart, and wherein the ball rollers (24, 26, 28, 30) of each row (20, 22) on one of two associated hollow throat-like inner ring raceways (50 54) and outer raceways (52; 56).

Description

Field of the invention

The invention relates to a ball roller bearing with a concentrically arranged to a longitudinal central axis inner ring and a coaxially surrounding outer ring, wherein a plurality of ball rollers whose geometry corresponds to a bilaterally symmetrically flattened ball with mutually parallel planar surfaces arranged in a first row and a second row are, in which the ball rollers in a first and a second, respectively comb-like sub-cage circumferentially equally spaced apart, and in which roll the ball rollers of each row on one of two associated cogged inner ring raceways and outer ring raceways.

Background of the invention

From the prior art ball roller bearings with balls flattened on both sides are known as rolling elements in a wide range of variation. Such bearings allow, inter alia, a reduced axial length of the same. In addition, these rolling elements allow a greater degree of filling of the rolling bearing compared to embodiments with spherical rolling elements. A disadvantage is, inter alia, that the ball rollers in the case of sudden changes in rotational speed, when falling below a minimum speed or during startup, inter alia, to undesirable wobbling or Entschränkungsbewegungen tend to the raceways. In order to reduce such effects, an expensive guidance of the ball rollers with axial ribs in conjunction with a cage for the ball rollers is usually necessary.

From the DE 10 2007 032 691 A1 For example, a single row ball roller bearing is known, which is composed essentially of an outer bearing ring and an inner bearing ring and a plurality of arranged between these bearing rings and held by a bearing cage in the circumferential direction at regular intervals to each other held ball rollers. The ball rollers have on the axial side in each case two flattened starting from a basic spherical shape and arranged parallel to each other end faces. With their outside of the end faces spherically curved treads roll the ball rollers on two each in the inside of the outer bearing ring and in the outside of the inner bearing ring recessed groove-shaped raceways. At least one of the raceways of the two bearing rings is axially bounded on both sides by circumferential thrust walls which are in operative connection with the end faces of the ball rollers and define a hollow rail-like rolling element guide in the circumferential direction, are prevented by the tumbling movements of the ball rollers occurring transversely to the running direction of the ball rollers.

Amongst other things, it is disadvantageous that at least one of the raceways has a production-technically complicated cross-sectional geometry deviating in sections from the circular arc shape in order to form an integrated shoulder as a first axial in-flight board. A second axial inrun is realized by a snap-in into an annular groove of the outer ring rigid locking ring, whereby a two-sided laterally-axial rebound of the thrust shelves in the occurrence of wobbling movements of the ball rollers is difficult.

Object of the invention

The invention has for its object to present a production technology easier to produce ball roller bearing in which the ball rollers are reliably guided under all operating conditions to avoid unwanted wobbling or Verschränkungsbewegungen.

Description of the invention

The solution to this problem is achieved with a ball roller bearing, which has the features of claim 1. Advantageous developments are defined in the dependent claims.

The invention accordingly relates to a ball roller bearing having an inner ring arranged concentrically with respect to a longitudinal center axis and an outer ring coaxially surrounding it, wherein a plurality of ball rollers, the geometry of which corresponds in each case to a symmetrically flattened ball on both sides with plane surfaces extending parallel to one another, in a first row and a second row are arranged, in which the ball rollers in a first and a second, respectively comb-like sub-cage circumferentially equally spaced from each other, and in which roll the ball rollers of each row on one of two associated cogged inner ring raceways and outer ring raceways.

To achieve the object, it is provided in this ball roller bearing, that in each case an annular groove is formed in a first outer end surface and a second outer end surface of the inner ring, that in the first annular groove a first thrust washer and in the second annular groove, a second thrust washer is arranged, and that between the first thrust washer and the first row of ball rollers and the second thrust washer and the second row of ball rollers each a disc-shaped insert is arranged.

As a result, a bordfreie and manufacturing technology advantageous, only hollow tongue-like or circular arc-shaped configuration of the cross-sectional geometry of the inner ring raceways and the outer ring raceways is required. The ball rollers also allow a reduction in the axial length of the double-row ball roller bearing. The disk-shaped inserts prevent in conjunction with the thrust washers unwanted wobbling of the ball rollers. A board-free cross-sectional contour of the raceways essentially follows in each case the curved sections of the cross-sectional geometry of the ball rollers and thus allows a manufacturing technology favorable production. The first part cage and the second part cage can each be designed, for example, as a rolling body-guided solid metal cage, as a rolling body-guided sheet metal cage, as a rolling body-guided solid plastic snap cage or as an inner ring-guided solid plastic snap cage, wherein these two sub-cages together form a cage system of the ball roller bearing. In addition, the ball roller bearing can be realized particularly cost-effective due to its high degree of symmetry with a variety of common parts.

According to an advantageous embodiment of this ball roller bearing is provided that the thrust washers each have an annular, pointing to the ball rollers thrust surface, which pass radially outward into a conical surface, that the first conical surface of the first thrust washer and the second conical surface of the second thrust washer are mutually oppositely inclined , And that abuts on the contact surfaces of each associated disc-shaped insert.

According to an alternative embodiment, it can be provided that the two thrust washers each have an annular, pointing to the ball rollers thrust surface on which rests the respective associated disc-shaped insert, and that these run-on surfaces radially outward in each case in an axial offset back in the direction of axially outwardly ,

The two last-mentioned design variants make it possible to avoid the disc-shaped inserts by axially outward rebounding the plane surfaces of the ball rollers, for example, their axes of rotation, especially in the case of abrupt changes in rotational speed and / or rotational direction of the ball roller bearing, falls below a minimum speed difference between the bearing inner ring and the bearing outer ring, or slightly tilt when restarting with respect to the longitudinal center axis of the ball roller bearing. By subsequent spring-back of the disc-shaped insert such a tilting of the ball rollers is completed quickly and especially low-friction and jamming. Furthermore, unwanted tumbling movements or Verschränkungsbewegungen the rolling elements are effectively terminated by their respective vertical axis or transversely to the inner ring and outer ring paths by a short-term axial spring back and forth of the depositors, so that the ball rollers return to their normal position transverse to the inner and outer raceways.

According to a technically advantageous development, it is provided that the first disc-shaped insert is arranged on a first cylindrical inner ring guide surface of the inner ring between the first annular groove and the first inner ring raceway, and that the second disc-shaped insert on a second cylindrical inner ring guide surface of the inner ring between the second annular groove and the second inner ring raceway is arranged. By preferably one-piece, circular disk-shaped inserts a reliable radial position securing the insert is given on the inner ring of the ball roller bearing.

In another favorable embodiment, it is provided that the disc-shaped inserts are made with a resilient-elastic material. As a result, a particularly effective and low-friction and low-wear axial guidance of the ball rollers is given. In addition, the spring-elastic insert without the need for structural changes allow compensation of any bearing tolerances. In addition, friction losses in the ball roller bearing can be further reduced by a friction-reducing coating of the preferably solid metal inserts. Alternatively, the disc-shaped inserts can be made of a low-friction plastic material with a sufficiently high mechanical strength, such as polytetrafluoroethylene (PTFE, Teflon ^® ) or the like, so that a friction-reducing coating of a metallic base body is dispensable.

list of figures

• 1 einen Längsschnitt durch ein erfindungsgemäßes, zweireihiges Kugelrollenlager gemäß einer ersten Ausführungsform,
• 2 eine perspektivische Ansicht des ersten Teilkäfigs des Kugelrollenlagers gemäß 1,
• 3 eine perspektivische Ansicht einer zweiten Ausführungsform eines ersten Teilkäfigs für das Kugelrollenlager gemäß 1,
• 4 eine perspektivische Ansicht einer dritten Ausführungsform eines Teilkäfigs für das Kugelrollenlager gemäß 1, und
• 5 einen Längsschnitt durch ein erfindungsgemäßes, zweireihiges Kugelrollenlager sehr ähnlich dem der 1, jedoch mit anderen Anlaufscheiben.

For a better understanding of the invention, the description several drawings are attached with several embodiments. In the drawings show:

• 1 a longitudinal section through an inventive, double-row ball roller bearing according to a first embodiment,
• 2 a perspective view of the first part of the cage roller bearing according to 1 .
• 3 a perspective view of a second embodiment of a first part of the cage roller bearing according to 1 .
• 4 a perspective view of a third embodiment of a sub-cage for the ball roller bearing according to 1 , and
• 5 a longitudinal section through an inventive, double-row ball roller bearing very similar to that of 1 , but with other thrust washers.

Detailed description of the drawings

The double row ball roller bearing 10 has an inner ring 12 and a coaxially surrounding outer ring 14 on, with the inner ring 12 and the outer ring 14 rotationally symmetrical to a longitudinal central axis 16 of the ball roller bearing 10 are arranged. The ball roller bearing 10 is in the axial direction on both sides symmetrical to a median plane 18 formed perpendicular to the longitudinal central axis 16 runs.

In a first row 20 and a second row 22 , the mirror symmetry to the median plane 18 run, similar ball rollers are arranged, of which only four ball rollers 24 . 26 . 28 . 30 you can see. The geometry of the ball rollers 24 . 26 . 28 . 30 the sake of a better graphical overview only by the example of the ball roller 30 be explained in more detail for the other, identical ball rollers. The ball roller 30 has two parallel spaced apart plane surfaces 32 . 34 perpendicular to a rotation axis 36 the ball roller 30 and mirror-symmetrical or axially equidistant from a median plane 38 the ball roller 30 run. The middle plane 38 runs perpendicular to the axis of rotation 36 the ball roller 30 , The remaining marked ball rollers 24 . 26 . 28 as well as the not shown in this view ball rollers have the same structural design as the ball roller described 30 on. The rolling elements serving as ball rollers 24 . 26 . 28 . 30 , whose geometry corresponds on both sides symmetrically flattened or flattened balls, among other things, allow a comparatively small axial length of the ball roller bearing 10 at the same load capacity as a conventional ball bearing. In addition, a higher degree of filling of the ball roller bearing 10 realizable.

The ballscrews 24 . 26 in the first row 20 are in a first, comb-like Teilkä 40 circumferentially evenly spaced apart, while the ball rollers 28 . 30 the second row 22 in a second, comb-like Teilkä 42 circumferentially evenly spaced from each other. Essentially hollow cylindrical foundations 44 . 46 the first and second part cages 40 . 42 lie on the back in the area of the median plane 18 of the ball roller bearing 10 adjacent to each other or are mirror-symmetrical to the median plane 18 of the ball roller bearing 10 positioned and together form a cage system 48 , By means of the cage system 48 of the ball roller bearing 10 Essentially, the circumferential positioning or spacing of the ball rollers takes place essentially alone 24 . 26 . 28 . 30 as well as all other ball rollers within the ball roller bearing 10 ,

The ballscrews 24 . 26 the first row 20 roll on a first inner ring track 50 and a first outer raceway 52 off, and the ball rolls 28 . 30 the second row 22 roll on a second inner ring track 54 and a second outer raceway 56 from. The same applies to the remaining ball rollers, not shown.

The mentioned inner and outer ring raceways 50 . 52 . 54 . 56 are each according to the invention board-free and formed like a hollow throat, in such a way that their circular arc-shaped cross-sectional geometry with the spherical surface geometry of the ball rollers 24 . 26 . 28 . 30 outside the flat plane surfaces 32 . 34 the same geometrically corresponds. As a result, in connection with the high degree of symmetry, a manufacturing technology particularly advantageous manufacturability of the inner ring 12 and the outer ring 14 of the ball roller bearing 10 given with a variety of identical parts. The inner ring 12 also has a rotationally symmetrical to the longitudinal central axis 16 trained, approximately cylindrical inner ring bore 58 for receiving a machine part, not shown, such as a shaft or the like.

In a first outer end face 60 and in a second outer end face 62 of the inner ring 12 is a first ring groove 64 and a second annular groove 66 formed with a respective substantially rectangular cross-sectional geometry. In the first ring groove 64 is an approximately hollow cylindrical first thrust washer 68 and in the second annular groove 66 is a substantially hollow cylindrical second thrust washer 70 arranged, with the two thrust washers 68 . 70 preferably axially flush with the outer end surfaces 60 . 62 of the inner ring 12 to lock. Between the first thrust washer 68 and the first row 20 with the ball rollers 24 . 26 there is a first disc-shaped insert 72 and between the second thrust washer 70 and the second row 22 with ball rollers 28 . 30 is accordingly a second disc-shaped insert 74 arranged. The two disc-shaped inserts 72 . 74 have a respective annular geometry, ie a hollow cylindrical geometry with a comparatively small axial extent. The two thrust washers 68 . 70 as well as the disc-shaped inserts 72 . 74 as well as the two partial cages 40 . 42 of the cage system 48 Due to their symmetry, they can advantageously be manufactured as identical parts.

The mechanical attachment of the thrust washers 68 . 70 in the ring grooves 64 . 66 of the inner ring 12 can be done for example by thermal shrinking, by gluing, by caulking or by a press-fit connection. The first depositor 72 is at a first inner ring guide surface 76 radially guided, and the second insert 74 is at a second inner ring guide surface 78 guided radially. The outer diameter of the two inserts 72 . 74 is such that these radially outside the radial inner circumferential surface 154 of the outer ring 14 Do not touch, so there is a sufficiently large distance is available. This guarantees their pivotability in the rolling bearing.

The two inner ring guide surfaces 76 . 78 each have an approximately cylindrical surface geometry. An axial clearance between the thrust washers 68 . 70 , the depositors 72 . 74 as well as the ball rollers 24 . 26 . 28 . 30 and all other not shown here ball rollers in the two rows of rolling elements 20 . 22 is preferably such that the most smooth, quiet and low-wear operation of the ball roller bearing 10 under all operating conditions.

The depositors 72 . 74 can be made with a spring-elastic material. This spring-elastic material may be, for example, a suitable metal, a metal alloy or a mechanically sufficiently strong and at the same time ideally as friction-reducing as possible plastic. Alternatively, the two depositors 72 . 74 also have a solid, so for example metallic core, which is at least partially coated with a suitable friction-reducing plastic, such as polytetrafluoroethylene (PTFE) or Teflon ^® or the like.

The first thrust washer 68 has radially inward a first annular, radially extending thrust surface 80 for the first disc-shaped insert 72 on, at the radially outward a conical surface 82 followed. The first contact surface 80 runs in this case orthogonal to the longitudinal central axis 16 of the ball roller bearing 10 while the cone surface 82 at an angle other than 90 ° to the longitudinal center axis 16 that is inclined. One of the better graphic overview half unsigned transition between the first contact surface 80 and the first cone surface 82 the first thrust washer 68 runs here approximately in the middle in relation to the radial height 88 the first thrust washer 68 , but alternatively it may also have a different radial position. Accordingly, the second thrust washer has 70 over a second contact surface 84 for the second depositor 74 and has a second cone surface 86 on, with the second cone surface 86 due to the symmetry of the ball roller bearing 10 deviating oppositely inclined to the first conical surface 82 is trained.

In the 1 are the ball rollers 24 . 26 . 28 . 30 in the so-called normal position, in which, for example, the two plane surfaces 32 . 34 the ball roller 30 parallel to the direction of the inner ring and outer ring raceway 54 . 56 of the ball roller bearing 10 run. Due to the invention slightly obliquely conical surfaces 82 . 86 the two thrust washers 68 . 70 can, for example, the second depositor 74 as with the arrow 90 indicated slightly feathers axially outward, for example, if the ball roller 30 around its axis of rotation 36 in relation to the longitudinal central axis 16 pivoted and / or when the ball roller 30 around its vertical axis 92 twisted and thus unwanted Verschränkungs- or tumbling movements takes place, which is substantially transverse to the inner ring and outer ring raceway 54 . 56 are oriented. Due to the axial spring action of the second insert 74 on the ball roller 30 The latter is returned to its normal position quickly, without friction and, above all, without the risk of jamming ball rollers. The same considerations apply to the operation of the first depositor 72 between the first row 20 with ball rollers 24 , 26 and the first thrust washer 68 , Such unwanted Verschränkungs- or tumbling movements occur in ball roller bearings or rolling bearings with spherical layer rolling elements often at the restart of the camp from hibernation, at abrupt speed changes of the bearing or falling below a bearing typical, minimum relative speed between the inner ring 12 and the outer ring 14 on.

Furthermore, axially on both sides in the outer ring 14 two holding grooves 94 . 96 educated. Radially opposite to the first holding groove 94 is in the first stop disk 68 a first groove 98 let in and the second thrust washer 70 has correspondingly opposite to the second holding groove 96 over a second groove 100 , In the first holding groove 94 is a first sealing element 102 fastened while in the second holding groove 96 a second sealing element 104 is attached. The two approximately disc-shaped sealing elements 102 . 104 are to achieve an optional seal of an interior 106 of the ball roller bearing 10 against unfavorable environmental influences in the fillets 98 . 100 the two thrust washers 68 . 70 either received without contact to form a narrow annular gap or creating a direct mechanical contact. The two sealing elements 102 . 104 are preferably formed with an elastomer such as a rubber material, silicone or the like.

2 shows a perspective view of the first part of the cage roller bearing of 1 , The comb-like, first Teilkä 40 has the rotational symmetry to the longitudinal central axis 16 designed, substantially hollow cylindrical body 44 , At the base body 44 of the first part cage 40 Here are just an example of thirteen similar cage bars 110 integrally formed, the circumferentially evenly to each other along the body 44 are positioned and each parallel to the longitudinal central axis 16 run as well as axially from the body 44 face away. The cage bars 110 limit thirteen pockets on the side 112 for the circumferentially evenly spaced leadership of the ball rollers 24 . 26 . 28 . 30 within the ball roller bearing according to 1 , wherein in each case two circumferentially immediately adjacent cage bars 110 a pocket 112 limit.

The second part cage of the cage system of the ball roller bearing of 1 is structurally identical to the first Teilkä only shown here 40 executed, this with its annular back 114 for the creation of the cage system 48 then congruent to a correspondingly configured rear side of the second sub-cage 42 abuts or mirror image of this in the ball roller bearing 10 is mounted.

The first Teilkä 40 Here, by way of example only, a solid-metal cage guided by a rolling element, which can be produced easily, for example, with the aid of machining production methods, with the aid of sintering methods or casting methods, is produced. It can be made with the same geometry but also as a sheet metal cage. Due to the predominantly peripheral and therefore subordinate management task of the cage system 48 for the ball rollers 24 . 26 . 28 . 30 this can be done without affecting the structural advantages of the ball roller bearing 10 from 1 can be easily realized with alternative cage types (cf. 3 . 4 ).

3 shows a perspective view of a second embodiment of a first part of the cage 120 for the ball roller bearing 10 according to 1 , This first Teilkä 120 comprises a rotationally symmetrical to the longitudinal central axis 16 trained annular body 122 , again at the thirteen not continuously designated and circumferentially evenly spaced cage bars 124 for the creation of an equal number of pockets also not always provided with reference numerals 126 are designed for circumferential guidance of the ball rollers.

The main body 122 this first part cage 120 has an approximately hollow cylindrical, radially inwardly directed, that is perpendicular to the longitudinal center axis 16 oriented ring flange 128 , to which a circumferential, parallel to the longitudinal central axis extending transition section 130 followed by an approximately quarter circular annular cross-sectional geometry. At the transition section 130 are parallel to the longitudinal central axis 16 running cage bars 124 integrally formed. By rearward arrangement of the annular flange 128 of the first part cage 120 to an annular flange of an identically formed, not shown here second sub-cage, in turn, the circumferential guidance of the ball rollers 24 . 26 . 28 . 30 within the ball roller bearing 10 from 1 necessary cage system 48 being constructed. In contrast to 2 is the first Teilkä 120 realized here as a wälzkörpergeführter sheet metal cage, which is particularly cost-effectively in production technology particularly for example by bending and punching from flat sheet metal semi-finished or the like in mass production suitable manner. part cages 120 according to 3 can be made with the same geometry but also as solid cages.

4 shows a perspective view of a third embodiment of a first part of the cage 140 for the ball roller bearing 10 according to 1 , This first Teilkä 140 comprises a rotationally symmetrical to the longitudinal central axis 16 trained, substantially hollow cylindrical body 142 , In turn, thirteen, for better clarity of the drawing, are not consistently designated, circumferentially evenly spaced caged webs 144 to provide an equal number of pockets, also not suffixed with reference numerals 146 for circumferential guidance of the ball rollers 24 . 26 . 28 . 30 educated. The thirteen pockets 146 are preferably each configured such that in each of the pockets 146 each a ball roller can be snapped and easily rotates.

The massive body 142 this first part cage 140 has one of the cage bars 144 opposite annular back 148 , A back of an identical to this first Teilkä 140 trained, not shown here second sub-cage can be used to create a cage system 48 for the ball roller bearing 10 according to 1 on the back congruent to the plant to the back 148 of the first part cage 140 brought and in the ball roller bearing 10 according to 1 to be assembled.

The first Teilkä 140 is here exemplarily designed as a wälzkörpergeführter, solid plastic snap cage. The first Teilkä 140 For example, it may be made from an optionally fiber-reinforced thermoplastic by known injection molding techniques using a suitable molding tool. Alternatively, thermosetting plastics with an optional fiber reinforcement can also be used. The same applies to the not shown, identical to the first Teilkä 140 trained second part cage

5 shows in a schematic longitudinal section through a ball roller bearing 10 ' according to a second embodiment, which is formed almost identical to the ball roller bearing 10 according to 1 , Unlike the latter, the two thrust washers 68 ' . 70 ' radially outside but no conical surfaces 82 . 84 rather, the axial distance to the respective associated, directly adjacent inserts 72 . 74 each by an axial offset 150 . 152 realized axially outward or paragraph, which is less expensive to produce than the mentioned cone surfaces 82 . 84 and has the same functionality.

LIST OF REFERENCE NUMBERS

10

Ball roller bearing (first embodiment)

10 '

Ball roller bearing (second embodiment)

12

inner ring

14

outer ring

16

Longitudinal central axis

18

Center plane of the ball roller bearing

20

First row of ball rolls

22

Second row of ball rolls

24

ball roller

26

ball roller

28

ball roller

30

ball roller

32

First plane

34

Second plane

36

Rotary axis of a ball roller

38

Center plane of a ball roller

40

First part cage

42

Second part cage

44

Basic body of the first part cage

46

Basic body of the second sub-cage

48

cage system

50

First inner ring raceway

52

First outer ring raceway

54

Second inner ring raceway

56

Second outer ring raceway

58

Inner ring bore

60

First outer end face of the inner ring

62

Second outer end face of the inner ring

64

First ring groove in the inner ring

66

Second annular groove in the inner ring

68

First thrust washer (second embodiment)

68 '

First thrust washer (second embodiment)

70

Second thrust washer (first embodiment)

70 '

Second thrust washer (second embodiment)

72

First depositor

74

Second depositor

76

First inner ring guide surface

78

Second inner ring guide surface

80

First contact surface

82

First cone surface

84

Second contact surface

86

Second cone surface

88

Radial height of thrust washers

90

arrow

92

Vertical axis of the ball roller

94

First hold

96

Second hold

98

First fillet

100

Second fillet

102

First sealing element

104

Second sealing element

106

inner space

110

cage web

112

bag

114

back

120

First part cage

122

body

124

cage web

126

bag

128

annular flange

130

Transition section

140

First part cage

142

body

144

cage web

146

bag

148

Back of main body

150

Return offset on the first thrust washer

152

Return offset on the second thrust washer

154

Radial inner lateral surface of the outer ring

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102007032691 A1 [0003]

Claims (7)

Ball roller bearings (10, 10 ') with an inner ring (12) arranged concentrically with respect to a longitudinal center axis (16) and an outer ring (14) coaxially surrounding it, wherein a plurality of ball rollers (24, 26, 28, 30) whose geometry corresponds to one on both sides symmetrically flattened ball with mutually parallel planar surfaces (32, 34), in a first row (20) and a second row (22) are arranged, wherein the ball rollers (24, 26, 28, 30) in a first and a second, each comb-like sub-cage (40, 42; 120; 140) are circumferentially equally spaced apart, and wherein the ball rollers (24, 26, 28, 30) of each row (20, 22) in one of two associated tuft-like Unroll inner ring raceways (50, 54) and outer ring raceways (52, 56), characterized in that in each case an annular groove (64, 66) is formed in a first outer end face (60) and a second outer end face (62) of the inner ring (12) s in the first annular groove (64) has a first thrust washer (68; 68 ') and in the second annular groove (66) a second thrust washer (70, 70') is arranged, and that between the first thrust washer (68, 68 ') and the first row (20) of the ball rollers (24, 26) and the second thrust washer (70; 70 ') and the second row (22) of the ball rollers (28, 30) each have a disc-shaped insert (72, 74) is arranged. Ball roller bearings after Claim 1 , characterized in that the thrust washers (68, 70) each have an annular, to the ball rollers (24, 26, 28, 30) facing thrust surface (80, 84), which pass radially outward into a conical surface (82, 86) in that the first conical surface (82) of the first thrust washer (68) and the second conical surface (86) of the second thrust washer (70) are inclined in opposite directions to one another, and in that the respectively associated disk-shaped inserts (72, 80, 84) 74) is present. Ball roller bearings after Claim 1 , characterized in that the thrust washers (68 ', 70') each have an annular, to the ball rollers (24, 26, 28, 30) facing thrust surface (80, 84), where the respectively associated disc-shaped insert (72, 74 ) is applied, and that the contact surfaces (80, 84) radially outward each in an axial offset back (150, 152) in the direction of axially outwardly pass. Ball roller bearing according to one of Claims 1 to 3 characterized in that the first disc-shaped insert (72) is disposed on a first cylindrical inner ring guide surface (76) of the inner ring (12) between the first annular groove (64) and the first inner ring raceway (50) such that the second disc-shaped insert (74) is arranged on a second cylindrical inner ring guide surface (78) of the inner ring (12) between the second annular groove (66) and the second inner ring raceway (54), and that the two inserts (72, 74) the radial inner lateral surface (154) of the outer ring (14 ) do not touch. Ball roller bearing according to one of Claims 1 to 4 , characterized in that the disc-shaped insert (72, 74) are made with a resilient-elastic material. Ball roller bearing according to one of Claims 1 to 5 , characterized in that the disc-shaped inserts (72, 74) consist of a metal and have a friction-reducing coating. Ball roller bearing according to one of Claims 1 to 6 , characterized in that the disc-shaped inserts (72, 74) consist of a low-friction plastic material.

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