DE102007060562A1 - Wheel bearing, in particular insert wheel bearing for commercial vehicles - Google Patents

Abstract

The invention relates to an insert wheel bearing for commercial vehicles, essentially consisting of a wheel hub (1) with a radial mounting flange (2), a journal (3) with a bearing seat (4) and two between the wheel hub (1) and the journal ( 3) arranged oblique rolling bearings (5, 6), whose outer bearing rings (7, 8) with their axially opposite end faces (9, 10) on a circumferential annular web (11) in the wheel hub (1) are pressed into its bore (12) and whose axially extended inner bearing rings (13, 14) with their axially opposite end faces (15, 16) are pressed against one another on the axle journal (3). In this case, between the outer bearing rings (7, 8) and the inner bearing rings (13, 14) of the angular rolling bearings (5, 6) in each case a plurality by two bearing cages (17, 18) in the circumferential direction at regular intervals held each other rolling elements (19, 20 , 21, 22) arranged with their running surfaces (23, 24, 25, 26) in the inner sides (27, 28) of the outer bearing rings (7, 8) and in the outer sides (29, 30) of the inner bearing rings ( 13, 14) incorporated raceways (31, 32, 33, 34 and 35, 36, 37, 38) roll. According to the invention, the rolling bodies (19, 20, 21, 22) of both angular rolling bearings (5, 6) are formed by ball rollers arranged side by side in two rows each with parallel pressure angle axes (39, 40, 41, 42), each being flattened symmetrically by a spherical basic shape as well as parallel ...

Description

Field of the invention

The The invention relates to a wheel bearing according to the preamble forming Features of claim 1, and in particular advantageous on insert wheel bearings for commercial vehicles as well as on all in O- or X-arrangement against each other employed skew bearings realizable.

Background of the invention

the It is common knowledge in the field of rolling bearing technology known that the wheel bearings on motor vehicles, the vehicle wheels on their journal in all driving conditions of the motor vehicle and the associated stresses of the wheel bearing exactly need to lead. The stress on the wheel bearings is influenced by a variety of factors, of which the wheel load, the roadway condition, the additional ones Strain during cornering and the driving time shares and the average Speeds in the individual driving conditions of special Meaning are. In addition, also influence the type of tires, the Fall of the wheel, the size of the braking forces and - with driven wheels - the On driving forces on the tire, the stress on the wheel bearing. Since these factors are difficult to detect, however, you attach stock selection and design especially during the most driving conditions of the motor vehicle the forces acting on the wheel bearing. Going away from there Therefore, have as wheel bearing types for light passenger vehicles especially double-row angular contact ball bearings of the first, second or third integration stage in single or tandem arrangement as particular proven suitable for heavy commercial vehicles especially in O arrangement against each other employed tapered roller bearings because of their high load capacity and wear resistance come into use. A particularly advantageous application of this Tapered roller bearings take place in the so-called insert wheel bearing, in this case for the wheel hub and the journal in a cost effective manner relatively soft metals or low-alloyed steels used and only the actual bearing components can be made out high-quality bearing steels are produced. In addition, a high-precision manufacturing of the inner causes Bearing rings of both tapered roller bearings that after assembly of the Bearing sets a specified bearing preload by itself, so that their elaborate manual adjustment is eliminated.

Such insert wheel bearing is for example from the DE 38 40 869 A1 and from the DE 10 2004 043 351 A1 previously known and consists essentially of a wheel hub with a radial mounting flange, a journal with a bearing seat and two arranged between the hub and the journal and in O arrangement against each hired, single-row tapered roller bearings whose outer bearing rings with their axially opposite end faces on a circumferential annular web in the wheel hub fitting pressed into the bore and the axially extended formed inner bearing rings are pressed against each other with their axially opposite end sides adjacent to the axle journal. Between the outer bearing rings and the inner bearing rings of the tapered roller bearings in each case a plurality of two bearing cages in the circumferential direction at regular intervals held tapered rollers are arranged, which roll with their treads on incorporated into the inner sides of the outer bearing rings and in the outer sides of the holding Ren raceways incorporated raceways ,

As It has already become known from other tapered roller bearing applications However, even with such an insert wheel bearing as disadvantageous proved that it is in special driving conditions of the motor vehicle to an unfavorable contact between the edges of the inner Bearing rings and the tapered rollers comes for a high Friction resistance in the wheel bearing and thus for a Derating and for increased fuel consumption of the Motor vehicle is the cause. In addition, require the elongated inner bearing rings of the tapered roller bearings such an insert wheel bearing overall a relatively large axial space and relatively high production costs and cause ultimately also an increase in the weight of the wheel bearing, which in a further undesirable way unsprung Increases masses on the motor vehicle and thus the rolling, spring and Steering comfort of the motor vehicle negatively affected.

Object of the invention

outgoing from the stated disadvantages of the known prior art Therefore, the invention is based on the object, a cost producible wheel bearing, in particular insert wheel bearing for Utility vehicles, to design in which the used Sliding bearings due to a low frictional resistance and a reduced axial space and the overall has a low weight.

Description of the invention

According to the invention, this object is achieved in a wheel bearing according to the Oberbe-handle of claim 1 such that the rolling elements of the two angular contact bearings used by each in Two rows of parallel Druckwinkelachsen juxtaposed ball rollers are formed, each having two symmetrically flattened from a spherical base and arranged parallel to each other side surfaces, which at the same time the bearing rings with an axially shorter overall length are executable by the flattened design of the rolling elements and the wheel bearing thereby a reduced weight having.

Of the The invention is therefore based on the finding that it is by use of two rows of ball rollers as rolling elements for the two angular roller bearings of the insert wheel bearing is possible, the previously with tapered rollers by sliding friction at the borders of the inner bearing rings resulting frictional resistance significantly reduce and at the same time the narrow construction as well the narrow track distances between the individual rows of rolling elements especially to use the inner bearing rings of the Slanting bearings axially shorter and therefore also easier to train in terms of mass. This is opposite single-row tapered roller bearings reduce axial by 10% to 20% Installation space with the same span and the same or higher axial load capacity and reduced by about 5% mass achievable for an insert wheel bearing with ball roller bearings.

preferred Embodiments and advantageous developments of the invention formed Wheel bearings are described in the subclaims.

After that it is according to claim 2 in the inventively designed Wheel bearing provided that the respective adjacent rolling elements of the two rows of each angular contact bearing with each other facing side surfaces immediately next to each other, respectively on common, perpendicular to the pressure angle axes running Transverse axes arranged and these side surfaces at the same time are designed as mutual guide surfaces. By This training will be the resulting on the ball rollers parallel Side surfaces simultaneously to an automatic mutual guidance of the ball rollers in their careers used, so that in connection with the with ball rolls constant rotation axes same and in cooperation with a corresponding bearing cage a otherwise probable in such rolling elements Cabinets or Quertaumeln can be almost excluded.

To Claim 3, it is a further feature of the invention formed Wheel bearing that the rolling elements of the two rows each skew bearing preferably different Have radii on their treads or alternatively both Rows of rolling elements with equal radii at their Treads are formed. With an insert wheel bearing a commercial vehicle by two, each with two rows of ball rollers trained Schrägwälzlager has it with regard to the radial and axial forces to be absorbed proved to be the most advantageous, the outer Rows of ball rollers starting from a larger one Ball basic shape with a larger radius at their To form treads and for the treads the inner rows of ball rollers starting from a smaller ball basic shape to provide a smaller radius. For other applications such Double row angular contact bearings or other Wheel bearings, however, may also be beneficial, any row of ball rollers with equal radii on their treads form or also the skew bearings with more than two rows form ball casters and the individual rows of ball rollers with equal and uneven radii on their treads form or the radii of the treads in others to combine possible shapes with each other.

According to claim 4, the inventively designed Wheel bearing also still characterized by the fact that the rolling elements the two rows of each skew bearing preferred have different widths between the side surfaces or alternatively with the same width between their side surfaces are formed. Also in this regard, it has a Insert wheel bearing of a commercial vehicle by two with each two rows of ball rollers trained skew bearings with regard to the radial and axial forces to be absorbed proved to be advantageous, the outer rows of Ball rollers starting from a larger ball basic shape with a larger width between their side surfaces form and for the treads of the inner Rows of ball rollers starting from a smaller ball basic shape to provide a smaller width between the side surfaces. However, it can also be used in other applications of such two-row Schrägwälzlagers or other wheel bearings be advantageous to train each row of ball rollers with the same width or in skew bearings with more than two rows of ball rollers, the individual rows of ball rollers with the same and uneven latitudes or their latitudes in others to combine possible shapes with each other.

An expedient development of the inventively embodied wheel bearing, it is further claim that the respectively arranged on common transverse axes rolling elements of the two rows of each Schrägwälzlagers are preferably arranged in common pockets of the preferably designed as a window cages bearing cages. This has proved to be particularly advantageous in that on the one hand the mutual guidance of the respective adjacent Wälzkör per both rows of each diagonal roller bearing is made possible and on the other hand at the same time the assembly costs for the wheel bearings are significantly reduced. However, should such a mutual guidance of the adjacent rolling elements not be provided, it is also possible to guide the ball rollers of the two rows of each angular roller bearing instead of common pockets of a window cage in the separate pockets of two comb or snap cages.

After all It is designed as an advantageous embodiment of the invention Wheel bearing by claim 6 nor suggested that the treads the rolling elements of the two rows of each angular contact bearing preferably the same radius as the groove-shaped Runways have in the bearing rings and with these in line contact stand. Such a training is therefore possible because the trained as ball rollers rolling elements unlike, for example, conventional bearing balls have a constant axis of rotation. The resulting line contact between the ball rollers and their groove-shaped raceways has the advantage that thereby a uniform Surface pressure with low voltage level between the ball rollers and the raceways with simultaneous increase the carrying capacity of each angular contact bearing is reached.

In summary has the inventively designed wheel bearing thus compared to those known from the prior art Wheel bearings have the advantage of being used by themselves of ball rollers as rolling elements with respect to tapered roller bearings by a minimized axial and radial installation space and by a low frictional resistance and a reduced weight same or increased load capacity. Since such ball rollers similarly inexpensive how conventional bearing balls are produced and also the manufacturing cost of inventively designed Angular contact bearing with that of angular contact ball bearings can be comparable, due to the reduced material costs and the reduced weight also of low production costs for the inventively designed Wheel bearing are assumed. In addition, through the line contact between the ball rollers and their raceways the tapered roller bearings from a high surface pressure and a high edge tension by the rolling elements resulting increased wear of the raceways the rolling elements effectively avoided, so that such trained skew bearings also increased Have life.

Brief description of the drawings

A preferred embodiment of the invention formed Wheel bearing will be described below with reference to the accompanying drawings explained in more detail. Showing:

1 a half-view of a cross section through an inventively designed wheel bearing;

2 the enlarged view of the angular contact bearings of the wheel bearing according to the invention according to detail X in 1 ,

Detailed description the drawings

Out 1 is clearly a trained as an insert wheel bearing wheel bearing for commercial vehicles, which essentially consists of a wheel hub 1 with a radial mounting flange 2 , a journal 3 with a La gersitz 4 and two between the wheel hub 1 and the journal 3 arranged and in O arrangement against each other employed skew bearings 5 . 6 consists. The outer bearing rings 7 . 8th this skew bearings 5 . 6 are doing with their axially opposite end faces 9 . 10 on a circumferential ring web 11 in the wheel hub 1 lying in the hole 12 pressed during the axially extended formed inner bearing rings 13 . 14 with their axially opposite end faces 15 . 16 abutting each other on the bearing seat 4 of the axle journal 3 are pressed on. In addition, between the outer bearing rings 7 . 8th and the inner bearing rings 13 . 14 the angular contact bearing 5 . 6 in each case a multiplicity by two bearing cages 17 . 18 in the circumferential direction at regular intervals held each other rolling elements 19 . 20 . 21 . 22 arranged, as in 2 can be seen with their treads 23 . 24 . 25 . 26 on in the insides 27 . 28 the outer bearing rings 7 . 8th and in the outsides 29 . 30 the inner bearing rings 13 . 14 integrated raceways 31 . 32 . 33 . 34 , and 35 . 36 . 37 . 38 roll.

Furthermore, by the in 2 shown enlarged view of the detail X according to 1 clearly that the rolling elements 19 . 20 . 21 . 22 both skew bearings 5 . 6 in each case in two rows with parallel pressure angle axes 39 . 40 . 41 . 42 juxtaposed ball rollers are formed, each two symmetrically flattened from a spherical base shape and arranged parallel to each other side surfaces 43 . 44 . 45 . 46 and 47 . 48 . 49 . 50 exhibit. The flattened formation of the rolling elements 19 . 20 . 21 . 22 makes it possible that the bearing rings 7 . 8th . 13 . 14 the angular contact bearing 5 . 6 can be executed with an axially shorter overall length and the entire wheel bearing is thus easier in terms of their mass. This is compared to single-row tapered roller bearings by 10% to 20% lower axial installation space with the same span and the same or higher radial and axial load capacity and reduced by about 5% mass for the wheel bearing achieved.

Likewise is off 2 it can be seen that the respective adjacent rolling elements 19 . 20 and 21 . 22 the two rows of each angular contact bearing 5 . 6 with their facing side surfaces 44 . 45 and 48 . 49 immediately nebenein other, each on common, perpendicular to the Druckwinkelachsen 39 . 40 . 41 . 42 extending transverse axes 51 . 52 arranged and these side surfaces 44 . 45 and 47 . 48 at the same time designed as mutual guide surfaces. This is in connection with the constant rotation of ball rollers and in cooperation with the bearing cages 17 . 18 a case of such rolling elements otherwise likely transverse staggering in their careers 31 . 32 . 33 . 34 , and 35 . 36 . 37 . 38 effectively avoided.

Only suggestively goes out 2 also apparent that the rolling elements 19 . 20 . 21 . 22 the two rows of each angular contact bearing 5 . 6 preferably different radii on their treads 23 . 24 . 25 . 26 have and with different widths between the side surfaces 43 . 44 . 45 . 46 and 47 . 48 . 49 . 50 are formed. With regard to the male radial and axial forces of the insert wheel bearing, it is most advantageous, the outer rows 19 . 22 the ball rollers starting from a larger ball basic shape with a larger radius at their treads 23 . 26 and a larger width between their side surfaces 43 . 44 and 49 . 50 form while the inner rows 20 . 21 the ball rollers starting from a smaller ball base on their treads 24 . 25 have a smaller radius and between their side surfaces 45 . 46 and 47 . 48 are formed with a smaller width. This is shown by the treads 23 . 24 . 25 . 26 the rolling elements 19 . 20 . 21 . 22 the two rows of each angular contact bearing 5 . 6 the same radius as their groove-shaped raceways 31 . 32 . 33 . 34 , and 35 . 36 . 37 . 38 in the bearing rings 7 . 8th . 13 . 14 on and with these in an advantageous line contact, through the even surface pressure with low stress level between the ball rollers and the raceways 31 . 32 . 33 . 34 , and 35 . 36 . 37 . 38 while increasing the carrying capacity of each angular contact bearing 5 . 6 is reached.

Finally is off 2 still evident that each on common transverse axes 51 . 52 arranged rolling elements 19 . 20 and 21 . 22 the two rows of each angular contact bearing 5 . 6 preferably in common bags 53 . 54 the exemplary trained as window cages bearing cages 17 . 18 are arranged. This has the advantage that on the one hand the mutual guidance of the respective adjacent rolling elements 19 . 20 and 21 . 22 both rows of each angular contact bearing 5 . 6 allows on the other hand at the same time the assembly costs for the wheel bearings are significantly reduced.

1

wheel hub

2

Mounting flange on 1

3

journal

4

Bearing seat on 3

5

Angular bearings

6

Angular bearings

7

outer bearing ring of 5

8th

outer bearing ring of 6

9

Front side of 5

10

Front side of 6

11

Ring bridge in 1

12

Bore of 1

13

inner bearing ring of 5

14

inner bearing ring of 6

15

Front side of 13

16

Front side of 14

17

Bearing cage of 5

18

Bearing cage of 6

19

Rolling elements in 5

20

Rolling elements in 5

21

Rolling elements in 6

22

Rolling elements in 6

23

Tread of 19

24

Tread of 20

25

Tread of 21

26

Tread of 22

27

Inside of 7

28

Inside of 8th

29

Outside of 13

30

Outside of 14

31

Career of 19 in 27

32

Career of 19 in 29

33

Career of 20 in 27

34

Career of 20 in 29

35

Career of 21 in 28

36

Career of 21 in 30

37

Career of 22 in 28

38

Career of 22 in 30

39

Pressure angle axis of 19

40

Pressure angle axis of 20

41

Pressure angle axis of 21

42

Pressure angle axis of 22

43

Side surface of 19

44

Side surface of 19

45

Side surface of 20

46

Side surface of 20

47

Side surface of 21

48

Side surface of 21

49

Side surface of 22

50

Side surface of 22

51

Transverse axis of 19 . 20

52

Transverse axis of 21 . 22

53

Bag of 19 . 20 in 17

54

Bag of 21 . 22 in 18

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• - DE 3840869 A1 [0003]
• DE 102004043351 A1 [0003]

Claims (6)

Wheel bearing, in particular insert wheel bearing for commercial vehicles, essentially consisting of a wheel hub ( 1 ) with a radial mounting flange ( 2 ), a journal ( 3 ) with a bearing seat ( 4 ) and two between the wheel hub ( 1 ) and the journal ( 3 ) arranged and in O-arrangement against each other employed skew bearings ( 5 . 6 ), whose outer bearing rings ( 7 . 8th ) with their axially opposite end faces ( 9 . 10 ) on a circumferential annular web ( 11 ) in the wheel hub ( 1 ) lying in the bore ( 12 ) are pressed and their axially extended formed inner bearing rings ( 13 . 14 ) with their axially opposite end faces ( 15 . 16 ) abutting each other on the journal ( 3 ) are pressed, wherein between the outer bearing rings ( 7 . 8th ) and the inner bearing rings ( 13 . 14 ) of the angular contact bearings ( 5 . 6 ) in each case a multiplicity by two bearing cages ( 17 . 18 ) in the circumferential direction at regular intervals held each other rolling elements ( 19 . 20 . 21 . 22 ) arranged with their treads ( 23 . 24 . 25 . 26 ) on the insides ( 27 . 28 ) of the outer bearing rings ( 7 . 8th ) and the outsides ( 29 . 30 ) of the inner bearing rings ( 13 . 14 ) incorporated raceways ( 31 . 32 . 33 . 34 , and 35 . 36 . 37 . 38 ), characterized in that the rolling elements ( 19 . 20 . 21 . 22 ) of both angular contact bearings ( 5 . 6 ) in each case in two rows with parallel pressure angle axes ( 39 . 40 . 41 . 42 ) arranged side by side ball rollers are formed, each two symmetrically flattened by a spherical base shape and arranged parallel to each other side surfaces ( 43 . 44 . 45 . 46 and 47 . 48 . 49 . 50 ), wherein by the flattened design of the rolling elements ( 19 . 20 . 21 . 22 ) at the same time the bearing rings ( 7 . 8th . 13 . 14 ) are executable with an axially shorter overall length and thus the wheel bearing has a reduced weight. Wheel bearing according to claim 1, characterized in that the respective adjacent rolling elements ( 19 . 20 and 21 . 22 ) of the two rows of each angular contact bearing ( 5 . 6 ) with their mutually facing side surfaces ( 44 . 45 and 48 . 49 ) immediately next to each other, each at a common, perpendicular to the pressure angle axes ( 39 . 40 . 41 . 42 ) transverse axes ( 51 . 52 ) and these side surfaces ( 44 . 45 and 48 . 49 ) are also designed as mutual guide surfaces. Wheel bearing according to claim 2, characterized in that the rolling bodies ( 19 . 20 . 21 . 22 ) of the two rows of each angular contact bearing ( 5 . 6 ) preferably different radii on their running surfaces ( 23 . 24 . 25 . 26 ) or alternatively both rows of rolling elements ( 19 . 20 . 21 . 22 ) with equal radii on their running surfaces ( 23 . 24 . 25 . 26 ) are formed. Wheel bearing according to claim 2, characterized in that the rolling bodies ( 19 . 20 . 21 . 22 ) of the two rows of each angular contact bearing ( 5 . 6 ) preferably different widths between their side surfaces ( 43 . 44 . 45 . 46 and 47 . 48 . 49 . 50 ) or alternatively with the same width between their side surfaces (FIG. 43 . 44 . 45 . 46 and 47 . 48 . 49 . 50 ) are formed. Wheel bearing according to claim 2, characterized in that in each case on common transverse axes ( 51 . 52 ) arranged rolling elements ( 19 . 20 and 21 . 22 ) of the two rows of each angular contact bearing ( 5 . 6 ) preferably in common pockets ( 53 . 54 ) preferably designed as window cages bearing cages ( 17 . 18 ) are arranged. Wheel bearing according to claim 2, characterized in that the running surfaces ( 23 . 24 . 25 . 26 ) of the rolling elements ( 19 . 20 . 21 . 22 ) of the two rows of each angular contact bearing ( 5 . 6 ) preferably the same radius as their groove-shaped tracks ( 31 . 32 . 33 . 34 , and 35 . 36 . 37 . 38 ) in the bearing rings ( 7 . 8th . 13 . 14 ) and are in line contact with them.