DE102006031956A1 - Double-row ball bearing for motor vehicle, has rows of bearing balls rolling between inner and outer rings, where row of balls are assigned to four-point-ball bearing and angular ball bearing, and inner ring is divided into path areas - Google Patents

Abstract

The bearing (1) has an inner ring (3) with two inner paths (18, 19), and an outer ring (2) with two outer paths. Rows of bearing balls (6, 7) rolls between the inner ring and the outer ring, where one row of the bearing balls (7) is assigned to a four-point-ball bearing (27) and another row of the bearing balls (6) is assigned to an angular ball bearing (26). The inner ring is divided in the two inner paths that are transverse to a bearing axis (23).

Description

Field of application of the invention

The The invention relates to a double row ball bearing with an inner ring with two inner raceways and an outer ring with two outer raceways, between which roll a first and a second row of bearing balls.

Background of the invention

Such a double-row ball bearing in the form of a tandem angular contact ball bearing is from the EP 1 105 662 B1 previously known. Under tandem arrangement is to understand in a professional way that the ball pressure lines of both rows of balls act in the same direction. In the 2 This bevel pinion shaft of a transfer case shown in this prior publication has a stepped shaft, at the rechtsseitigem end of the bevel pinion 4 lies. In the case 1 is the bevel pinion shaft 5 over two spaced apart tandem angular contact ball bearings 16 . 17 held, each one-piece bearing inner rings 18 and one-piece bearing outer rings 19 each having two shoulders 20 . 21 have. The bearing balls 22 and 23 show inside the warehouse 16 and 17 the same size and are each in bearing cages 24 guided. The figure is further removable that within a warehouse 16 . 17 the unspecified raceways of the bearing balls 22 . 23 have a different diameter. Because near the bevel pinion 4 The largest radial and axial loads occur is the tandem angular contact ball bearings 16 much larger dimensions than the tandem angular contact ball bearings 17 , Due to the O arrangement of the two tandem angular contact ball bearings 16 and 17 to each other it is ensured that each one of the bearings 16 . 17 The force can absorb in an axial direction, ie, an axial displacement of the bevel pinion shaft 5 can not.

The disadvantage here is that each of the two tandem angular contact ball bearings 16 . 17 can only absorb axial force in one direction. This means that for the axial fixing of the bevel pinion shaft, two spaced tandem angular contact ball bearings 16 and 17 must be used, which requires a significantly increased axial space.

Also from the DE 84 05 082 U1 Such a double-row ball bearing in the form of a double angular contact ball bearing is already known. In the 1 to 6 various embodiments are shown in the drawing. However, the double angular contact ball bearings described there are only able to absorb axial forces from one direction. This concrete statement goes out of hand 6 of this document, which states that in all embodiments, the force from the outside attacks from the top left, while the counterforce is right down. Well, while in the 5 and 6 a split inner ring shown, but must be performed divided to the camp to be able to put together. This is the page 9 removable, in which it is stated that both ball cages 40 . 41 must be used in a raceway. But this is only possible if the inner race is made split. Accordingly, this prior publication of the skilled person can not find any reference to a four-point ball bearing.

In this context is from the 4 . 5 and 6 of the EP 1 443 228 A1 the storage of a bevel pinion shaft has become known, in which the bearing consists of three rows of balls, which have a common outer ring and a split inner ring. In the region of the largest load, ie, in the region of the bevel pinion, two bearing balls are arranged side by side, the ball pressure lines extend in one direction, ie, the two rows of balls are arranged zuein other tandem and the pressure angle have the same warping. Spaced in the axial direction of a third row of balls is present, the ball pressure line is exactly in the other direction, wherein both rows of balls are employed to each other in O arrangement. This ensures that the bevel pinion shaft can not be moved in any of the two axial directions. The disadvantage here is that even this solution requires a relatively large axial space due to their three spaced ball races.

Summary of the invention

outgoing from the disadvantages of the known prior art is the invention Therefore, the task of developing a generic ball bearing, the optimal to given load conditions is adjustable in both the axial and in the radial direction and that about it It is also easy to produce and handle. Another The object of the invention is to provide such storage as possible space to design sparingly.

According to the invention this Task according to the characterizing part of claim 1 in conjunction solved with the preamble in that the first row of Bearing balls is assigned to a four-point ball bearing, wherein the Inner ring formed in the raceway area divided transversely to a bearing axis is.

Four-point ball bearings have in a known manner on the inner ring and the outer ring two circular arc-shaped raceways, the centers of curvature are offset from each other so that the balls be the races under load in four points stir. One of the two races, mostly the inner ring, is split so that the balls can be filled. The bearings are particularly suitable for changing, purely axial load or overwhelming axial load.

This Four-point ball bearing is now in accordance with the invention with other ren ball bearing types combined to adapt to different load cases to be able to. Thus, for example, according to claim 2, that the second row the bearing balls associated bearing is an angular contact ball bearings. Angular contact ball bearings take in known sage only in one direction axial forces, so with this combination of four-point ball bearings and angular contact ball bearings Such a combination of bearings is particularly suitable if the main forces acting in one axial direction, in the opposite axial Direction the force to be collected but much lower.

To Claim 3 is assigned to the second row of bearing balls Bearings be a deep groove ball bearing. For deep groove ball bearings, the Bearing balls in the inner and outer ring guided in deep grooves. The radial and axial load capacity is alike high, they also have the highest Speed limits of all types of bearings. The combination four-point ball bearing and deep groove ball bearings is particularly advantageous applied when the main part of the take up bearing forces in radial Direction lies, but at the same time to absorb axially acting forces are.

To Another feature of the invention according to claim 4 is the second Row of bearing balls associated bearing a shoulder ball bearing be. Shoulder ball bearings are very similar in construction to the deep groove ball bearing. They differ only in the outer ring by the existing one Shoulder. The raceway profile is one-sided on the groove bottom in a short cylindrical track over.

To Another feature of the invention according to claim 5, it is also possible that the bearing associated with the second row of bearing balls also is a four-point ball bearing, with the inner ring in the raceway area in this case also formed divided transversely to the bearing axis. In other words, in this particular case, the bearing inner ring designed in three parts.

Further Features of the invention will become apparent from the claims 6 and 7.

To Claim 6 is provided that the bearing balls have the same or have a different diameter, while it is apparent from claim 7, that the bearing balls have the same or different pitch circle exhibit. Through this combination of different sized Bearing balls and differently sized pitch circle diameters in turn can be acted on the respective applications, i. e., The bearing can be optimally adapted to the given operating conditions be adjusted.

To Another feature of the invention according to claim 8, the bearing balls in a cage be held, this according to claim 9 at least one axial end is provided with a radially directed retaining lug, in an associated Groove engages one of the bearing rings. By the use of the bearing cages is while facilitating the assembly of the overall bearing assembly in a known manner and the balls are kept at a distance from each other. With help the retaining lug and its snapping into a groove of one of the bearing rings has the advantage that the composite of several components Bearing assembly is held together captive.

Brief description of the drawings

Further Features of the invention will become apparent from the following description and from the drawings, in which embodiments of the invention are shown simplified.

It demonstrate:

1 a longitudinal section through an inventive bearing with the combination four-point ball bearing angular contact ball bearings,

2 a longitudinal section through an inventive ball bearing with the combination four-point ball bearing deep groove ball bearings,

3 a longitudinal section through an inventive ball bearing with the combination four-point ball bearing shoulder ball bearings,

4 a longitudinal section through an inventive ball bearing with the combination four-point ball bearing four-point ball bearings and

5 a longitudinal section through a gear with one of the inventions bearing combinations.

Detailed description of the drawings

This in 1 illustrated ball bearings 1 consists of the outer ring 2 and the inner ring 3 between those in cages 4 . 5 guided bearing balls 6 . 7 roll off. The outer ring 2 own the shoulders 8th . 9 . 10 so that outer races 11 and 12 are formed. The outer raceway 11 the bearing balls 6 gets through the shoulder 8th posed while the rillenförmi ge outside career 12 by the two axially spaced apart shoulders 9 and 10 is limited. To the ball bearing 1 heard further the inner ring 3 , which consists of the two partial rings 13 and 14 is composed. The partial ring 13 again has two axially spaced apart shoulders 15 . 16 on, leaving the inner raceways 17 . 18 for the bearing balls 6 . 7 are formed. The other associated inner raceway 19 becomes of the partial ring 14 put, with the two partial rings 13 . 14 in the parting plane 20 lie together.

The bearing balls 6 . 7 have a different diameter and a different pitch circle radius 21 . 22 on, wherein under pitch radius in a known manner, the radial distance from the bearing axis 23 to the center of the bearing balls 6 . 7 to understand. From this it is derived that the circle radius 21 greater than the pitch circle radius 22 is. As you can see, the cage works 5 the left side bearing balls 7 with his holding nose 24 in a circumferential groove 25 of the partial ring 13 one. The ball bearing 1 is therefore made of the right angular contact ball bearings 26 and the left side arranged four-point ball bearing 27 together.

As can be seen further, the angular contact ball bearing 26 the pressure angle α, the of the pitch radius 21 and from the ball pressure line 28 is limited. The four-point ball bearing 27 has the pressure angle β1, which in the present case of the pitch radius 22 and from the ball pressure line 29 is formed. Both ball pressure lines 28 . 29 run parallel to each other and meet at an unspecified point on the bearing axis 23 , To the four-point ball bearing 27 naturally belongs to the pressure angle β2, which in turn of the pitch radius 22 and from the ball pressure line 30 is formed. This means that the pressure angles α and β1 have the same sign, while the pressure angle β2 has a negative sign. This ball bearing 1 is very similar to the well-known tandem angular contact ball bearings, but in contrast to this it can absorb axial forces in both directions and also radial forces. The axial main load is represented by the right-hand arranged strong arrow, while the left-side male axial counterforce is much lower, which is illustrated by the somewhat thinner arrow in the drawing.

Classic application for this from the four-point ball bearing 27 and the angular contact ball bearing 26 composite bearings 1 is, for example, the storage of a bevel pinion shaft in a transfer case for motor vehicles, the bevel pinion shaft for simplicity's sake, however, is not shown in the drawing. In train operation, high axial and radial forces are transmitted to the bearing when transmitting the full torque due to the helical toothing of the bevel pinion 1 transfer. This situation corresponds to the strong arrow arranged on the right, with the forces emanating from the bevel pinion shaft from the partial ring 13 over its inner raceways 17 and 18 on the outer ring 2 over its outer raceways 11 . 12 be transmitted. In overrun, which represents the left side arranged thinner arrow, the male moments are much lower, but changes the sign of the axial force. This means the lower axial force is now passing through the subring 14 on the inner raceway 19 and the bearing ball 7 On the shoulder 9 of the outer ring 2 transfer. It is obvious that by varying the size of the bearing ball 6 . 7 , as well as their pitch circle radius 21 . 22 and variation of the pressure angles α, β1 and β2 different bearing modifications can be compiled, which are adapted to the particular application in a very accurate manner. The pressure angle α can assume a value between 5 and 40 degrees and the pressure angles β1 and β2 a value between 5 and 30 degrees, wherein β1 and β2 can also differ in size from one another.

This in 2 illustrated ball bearings 31 is different from the one in 1 in that instead of the angular contact ball bearing 26 a deep groove ball bearing 32 is arranged on the right side. This means that the outer raceway 11 through the extra shoulder 34 and the inner raceway 17 through the extra shoulder 33 is limited. This Lageranordndung will be particularly useful when the main load of the attacking forces occurs in the radial direction, while only relatively small forces are to be absorbed in the axial direction. These in turn are in both directions by the four-point ball bearing described in detail above 27 and the deep groove ball bearing 31 collected.

This in 3 illustrated ball bearings 35 is different from the one in 1 illustrated ball bearings 1 only by the fact that the bearing balls 6 . 7 an equal circle radius 21 . 22 exhibit and in a common cage 36 are housed. One-piece cages are useful, provided that the pitch circle and bearing ball diameter are coordinated so that the relative speeds of both rows of balls is equal.

This in 4 illustrated ball bearings 37 is characterized by the fact that two four-point ball bearings 27 . 38 are arranged side by side. This has the consequence that in this embodiment, the inner ring 3 into three separate components, namely the partial ring 40 who is the inner race 42 forms the partial ring 41 who has the inner raceways 43 and 18 represents and the subring 14 who in turn is the inner-career 19 provides. As arranged on the left side Four point ball bearings 27 is also on the right side angeordenten four-point ball bearing 38 the separation of the inner ring 3 in the field of inner raceways 42 . 43 performed.

Finally, in 5 a bearing assembly shown, the ball bearing 35 according to 3 like. The only difference is that in this embodiment, the outer ring 2 is omitted because the inner contour of a gear 44 which is on the hollow shaft 45 is arranged, the outer ring 2 replaced.

1

ball-bearing

2

outer ring

3

inner ring

4

Cage

5

Cage

6

bearing ball

7

bearing ball

8th

shoulder

9

shoulder

10

shoulder

11

Outer race

12

Outer race

13

partial ring

14

partial ring

15

shoulder

16

shoulder

17

Inner raceway

18

Inner raceway

19

Inner raceway

20

parting plane

21

Pitch radius

22

Pitch radius

23

bearing axle

24

retaining nose

25

groove

26

Angular contact ball bearings

27

Four-point contact ball bearings

28

Ball pressure line

29

Ball pressure line

30

Ball pressure line

31

ball-bearing

32

Deep groove ball bearings

33

shoulder

34

shoulder

35

ball-bearing

36

Cage

37

ball-bearing

38

Four-point contact ball bearings

39

parting plane

40

partial ring

41

partial ring

42

Inner raceway

43

Inner raceway

44

gear

45

hollow shaft

α

contact angle

β1, β2

contact angle

Claims (9)

Double row ball bearing ( 1 . 31 . 35 . 37 ) having an inner ring with two inner raceways and an outer ring with two outer raceways, between which a first and a second series of bearing balls ( 7 . 6 ), characterized in that the first row of bearing balls ( 7 ) a four-point ball bearing ( 27 ), wherein the inner ring ( 3 ) in the career area ( 18 . 19 ) transverse to a bearing axis ( 23 ) is formed divided. Double row ball bearing ( 1 . 35 ) according to claim 1, characterized in that that of the second row of bearing balls ( 6 ) associated bearings an angular contact ball bearing ( 26 ). Double row ball bearing ( 31 ) according to claim 1, characterized in that that of the second row of bearing balls ( 6 ) associated bearings a deep groove ball bearing ( 32 ). Double row ball bearing according to claim 1, characterized characterized in that associated with the second row of bearing balls Bearing is a shoulder ball bearing. Double row ball bearing ( 37 ) according to claim 1, characterized in that that of the second row of bearing balls ( 6 ) associated bearing a four-point ball bearing ( 38 ), wherein the inner ring ( 3 ) in the career area ( 42 . 43 ) transversely to the bearing axis ( 23 ) is formed divided. Double row ball bearing ( 1 . 31 . 35 . 37 ) according to claim 1, characterized in that the bearing balls ( 6 . 7 ) have the same or a different diameter. Double row ball bearing ( 1 . 31 . 35 . 37 ) according to claim 1, characterized in that the bearing balls ( 6 . 7 ) have the same or different pitch circle radius ( 21 . 22 ) exhibit. Double row ball bearing ( 1 . 31 . 35 . 37 ) according to claim 1, characterized in that the bearing balls ( 6 . 7 ) in a cage ( 4 . 5 . 36 ) are held. Double row ball bearing ( 1 ) according to claim 8, characterized in that at least one of the bearing cages ( 5 ) at one axial end with little least one radially directed retaining lug ( 24 ) provided in an associated groove ( 25 ) one of the bearing rings ( 3 ) intervenes.