DE102018101912B3 - The wheel bearing assembly - Google Patents

Abstract

Wheel bearing arrangement comprising a wheel bearing designed as an angular contact ball bearing or tapered roller bearing which comprises rolling elements guided between a torsionally rigid bearing part and a rotatable bearing part (21) connected to a wheel bearing flange (20), the wheel bearing flange (20) facing the wheel bearing, with a radially extending contact section (FIG. 30) is formed, and the rotatable bearing part (21) has a Wälzkörperlaufbahn, in which in the direction of Radlagerflansches (20) an axially extending, a spin plate (22) receiving, receiving portion (28) adjacent, wherein the spin plate (22) a a first, substantially axially extending portion (23) and a second, substantially radially extending portion (25), which are arranged at an angle to each other, wherein the first portion (23) and the second portion (24) respectively a bending edge (26, 27) with an intermediate portion (24) are connected, thereby geken nzeichnet that in the receiving portion (28) a radial, circumferentially formed groove (29) is arranged, which extends in the axial direction in sections below the first portion (23) of the spin plate (22) and in the direction of Radlagerflansches (20) behind the Bending edge (26) of the first section (23) ends

Description

Field of the invention

The invention relates to a wheel bearing arrangement with a designed as angular contact ball bearings or tapered roller bearing, which comprises between a torsionally rigid bearing part and connected to a Radlagerflansch rotatable bearing part rolling elements, wherein the Radlagerflansch facing the wheel bearing, is formed with a radially extending contact portion and the rotatable bearing part a Wälzkörperlaufbahn having, in the direction of the Radlagerflansches an axially extending, a slinger receiving, receiving portion adjacent. The spinner plate has a first, substantially axially extending portion and a second, substantially radially extending portion, which, connected by an intermediate portion, are arranged at an angle to each other. With the intermediate portion of the first portion and the second portion are each connected by a bending edge.

State of the art

In the case of wheel bearings, it must be ensured that neither solid particles nor corrosive media can penetrate into this space by sliding the seal on both sides of the raceways and rolling elements on both sides, filled with lubricant. Since slight transverse tilts can occur within the bearing during lateral acceleration, there is a risk that the lip seals used will lift off the sliding surfaces. The seals used may cooperate with a spin plate made of formed sheet metal. The spin plate connected to a rotating wheel hub or a wheel bearing flange can form an additional sealing labyrinth together with another metal ring arranged in a stationary part of the wheel suspension. In addition, sealing lips extend at least one sealing ring in the axial or radial direction and are slidably guided on the centrifugal plate. The abovementioned components of the seal can also be an integral part of a sealing cassette in which the sealing lips are defined axially prestressed.

Axial vehicle side on the wheel bearing is a mainly axially directed opening between the participating partners Drehund, which is occasionally covered by a joint bell of the adjacent constant velocity joint. Axial wheel flange side is the opening between the partners of the wheel bearing, due to the immediately adjacent wheel flange, directed radially outward and very easy to reach for splashing. Since a metal sheet lintel on the wheel flange leads to a better sliding sealing contact than the usually untreated or merely ground wheel flange inside, a centrifugal plate is mounted adjacent to the wheel flange before installation of the wheel bearing on the wheel hub. The spin plate is made of a higher quality material than the wheel flange, such as a stainless steel. The spin plate may also consist of a steel sheet whose surface is treated, for example galvanized or coated.

Slippage of the slinger can be triggered by vibration, sustained vibration loads or other causes, whereby the slinger on the outer surface axially approaches the rolling elements and damage them in contact. This leads to a failure of the wheel bearing.

From the DE 10 2013 218 635 A1 a wheel bearing assembly is known, comprising a designed as angular contact ball bearings or tapered roller bearing wheel bearing, which comprises between a torsionally rigid bearing part and a connected to a Radlagerflansch rotatable bearing part guided rolling elements. The wheel bearing flange facing the wheel bearing is formed with a radially extending abutment portion. The rotatable bearing part has a rolling body raceway, against which an axially extending, a splash plate receiving, receiving portion adjacent in the direction of Radlagerflansches, wherein the spin sheet has a first, substantially axially extending portion and a second, substantially radially extending portion which, connected by an intermediate portion, are arranged at an angle to each other, with which the first portion and the second portion are each connected by a bending edge. For a stationary fixation, the centrifugal plate is in contact with the contact area of the wheel flange on the one hand with line or surface contact. On the other hand, the second portion of the centrifugal plate is pressed onto the receiving portion of the torsionally rigid bearing part. For axial securing, the first section of the centrifugal plate locks at the end on a radially extending, circumferential step, which is arranged adjacent to the Wälzkörperbahn. For this purpose, the first section must be pressed over the step when pressing by a mounting tool, so that a locking is achieved. During assembly, the problem may arise that the first portion of the spin plate is not completely pressed during pressing over the step, so that the spin plate in the axial direction is not sufficiently secured or there may be an axial play, which is due to manufacturing tolerances, what can lead to a gap.

Disclosure of the invention

It is an object of the present invention to develop a wheel bearing assembly of the type mentioned, which is characterized by a simplified assembly of the slinger and prevents accidental wandering of the slinger.

This object is solved by the features of independent claim 1. Advantageous embodiments are given in the claims dependent thereon, which in themselves or in various combinations with each other can represent an aspect of the invention.

Thereafter, a wheel bearing assembly is proposed with an executed as angular contact ball bearings or tapered roller bearing wheel bearing, which comprises between a torsionally rigid bearing part and a connected to a Radlagerflansch rotatable bearing part guided rolling elements. The wheel bearing flange facing the wheel bearing is formed with a radially extending abutment portion. The rotatable bearing part has a rolling body running track, against which an axially extending, a spin plate receiving, receiving portion adjacent in the direction of Radlagerflansches. The spinner plate has a first, substantially axially extending portion and a second, substantially radially extending portion, which, connected by an intermediate portion, are arranged at an angle to each other. With the intermediate portion of the first portion and the second portion are each connected by a bending edge. In order to simplify the assembly of the centrifugal plate and to prevent unintentional wandering of the centrifugal plate, the invention provides that in the receiving portion a radial circumferentially formed groove is arranged, which extends in the axial direction in sections below the first portion of the centrifugal plate and in the direction of Radlagerflansches behind the bending edge of the first section ends. When pressing the slinger, the bending edge of the first section springs into the groove, which allows overpressing of the bending edge, whereby a comparable holding effect is achieved, as in the locking of the slinger at the stage according to the DE 10 2013 218 635 A1 the case is. The groove in the region of the bending edge allows the overpressure, so that the pressing force of the mounting tool acting on the intermediate portion causes a compression of the bending edge in the direction of the groove. In the region of the bending edge, the stiffness of the centrifugal plate is greatest, so that in this area the highest contact pressure to the rotatable bearing part is present. Forces introduced into the slinger by microvibrations would have to build up a voltage in the region of the bending edge in order to cause the bending edge to spring back.

In contrast to the embodiment according to the DE 10 2013 218 635 A1 Thus, it is possible to eliminate the step over which the first section of the centrifugal plate is to be moved completely away, whereby the assembly process is simplified and becomes more reliable.

In particular, the groove in the receiving portion may have one or more radii. As a result, a better stress distribution in the rotatable bearing part can be achieved.

According to an advantageous development, the groove in the receiving portion may have a depth which corresponds approximately to the material thickness of the slinger.

According to an advantageous development, the groove in the receiving portion may have a depth which corresponds approximately to the overlap of an interference fit.

Preferably, the groove in the receiving portion having a groove depth corresponding to the material thickness and the overlap of the interference fit.

Furthermore, a further groove may be arranged on the contact section, which section extends below the second section of the centrifugal plate and ends in the direction of the receiving section ends behind the bending edge of the second section. In this way, over-pressing of the centrifugal plate in the axial direction can be promoted, whereby the flat abutment of the second section on the contact section of the wheel bearing flange can be ensured. An only line-shaped concerns of the second section can thus be avoided.

According to a preferred development, the first section of the centrifugal plate for axial securing can additionally be supported on a, in particular circumferential, projection. By over-pressing the spin sheet in the region of the bending edges in the respective groove in the receiving portion and the contact portion during the press-in ensures that the first portion is pressed over the projection and locked when moving out of the mounting tool with the projection.

Preferably, the intermediate portion of the centrifugal plate may be formed as a specific contact surface for a mounting tool. This allows the take-up of the slinger by an assembly tool for automated assembly, in order to press the sling on the receiving portion until an axial position is reached, in which the bending edge springs into the groove of the receiving portion.

According to a preferred refinement, a further profiled section, which extends in sections in the direction of the torsionally rigid bearing part, can adjoin the second section of the centrifugal plate. For this purpose, the profiled portion cooperate with a sealing set, which is arranged on the torsionally rigid bearing part.

Furthermore, a sealing means can be arranged in a cavity which forms between the wheel bearing flange and the spin plate. The sealing means can serve to seal a self-adjusting annular gap between the centrifugal plate and the rotatable bearing part. For this purpose, the sealant may be designed as a plastic or elastic mass. The sealing means may also be formed as a sealing lip, which is arranged by a cohesive connection to the rotatable bearing part in the region of the forming cavity.

The invention is not limited to the specified combination of the features of the independent patent claim 1 and the claims dependent thereon. In addition, there are further possibilities of combining individual features, in particular if they result from the patent claims, the following description of the exemplary embodiments or directly from the figures. In addition, the reference of the claims to the figures by the use of reference numerals is not intended to limit the scope of the claims to the illustrated embodiment examples.

list of figures

• 1 einen Ausschnitt eines Radlager 1 gemäß dem Stand der Technik;
• 2 eine schematische Darstellung eines Ausführungsbeispiels einer erfindungsgemäßen Radlageranordnung;
• 3 eine schematische Darstellung eines zweiten Ausführungsbeispiels einer erfindungsgemäßen Radlageranordnung; und
• 4 eine schematische Darstellung eines dritten Ausführungsbeispiels einer erfindungsgemäßen Radlageranordnung.

For further explanation of the invention reference is made to the drawings, in which different embodiments are shown simplified. Show it:

• 1 a section of a wheel bearing 1 according to the prior art;
• 2 a schematic representation of an embodiment of a wheel bearing assembly according to the invention;
• 3 a schematic representation of a second embodiment of a wheel bearing assembly according to the invention; and
• 4 a schematic representation of a third embodiment of a wheel bearing assembly according to the invention.

Detailed description of the drawing

In the 1 is a section of a wheel bearing 1 according to the prior art, which is intended for a vehicle (not shown). This is the construction of a wheel bearing seal 2 shown one as a spin plate 3 trained pre-seal and a sealing set 4 includes. The wheel bearing 1 includes as a torsionally rigid bearing part 5 an outer stationary positioned bearing ring, which is connected in the installed state with a wheel carrier (not shown). rolling elements 6 are outside of the bearing part 5 and on the inside on a rotatable bearing part 7 , guided an inner bearing ring, which is integral with a radially oriented Radlagerflansch 8th connected is.

The sling made of a metallic material 3 is by means of a line contact or surface contact on the one hand via a support zone 10 on a radially oriented contour, the wheel bearing flange 8th , as well as by an inner flexurally elastic attachment portion 11 on a largely cylindrical contour 12 the hub of the rotatable bearing part 7 supported. Between these contact points the slinger runs 3 under formation of a cavity 13 spaced to an inner radius 9 the rotatable bearing part 7 ,

A defined preloaded mounting position is achieved by the spin plate 3 at one in the second bearing part 7 introduced stage 14 with its attachment section 11 locked. This is intended to a hiking of the slingshot 3 be avoided due to micro-movements in the direction of the rolling elements. This is the spin plate 3 by means of a tool on the cylindrical contour 12 pressed. When installing the slinger 3 may be the problem that the attachment section 11 when pressing in not completely over the step 14 Pressed away, so that the attachment section 11 not locked and the spin plate 3 the required preload is missing.

The representation in 2 shows a schematic representation of an embodiment of a wheel bearing assembly according to the invention, wherein only one with a Radlagerflansch 20 connected rotatable bearing part 21 is shown. The wheel bearing flange 20 can be integral with the rotatable bearing part 21 be connected. Adjacent to a rolling body track, not shown, on the rotatable bearing part 21 there is a cylindrical receiving portion 28 which sections in the axial direction of the rotatable bearing part 21 extends. The cylindrical receiving portion 28 may have a conical shape. At the wheel bearing flange 20 is a sectionally radially extending contact section 30 intended.

On the recording section 28 is a preferably made of a metallic material slinger 22 pressed. The spin plate 22 has a first substantially axially extending cylindrical portion 23 and a second, substantially radially extending, disk-shaped portion 25 on, which by an intermediate section 24 are arranged at an angle to each other. At least the first section 23 is flexurally elastic. Also preferred are the intermediate section 24 and the second section 25 flexurally elastic. The intermediate section 24 is with the first section 23 and the second section 25 each by a bending edge 26 . 27 connected are the intermediate section 24 is in mounted position of the slinger 22 at least partially spaced from the Radlagerflansch 20 arranged so that at least in a transition area 31 between the receiving section 28 and the investment section 30 as well as the intermediate section 24 a cavity 32 formed.

In the recording section 28 of the storage part 21 is a radial, circumferentially formed groove 29 is arranged, which in the axial direction sections below the first section 23 of the slinger 22 in the direction of the wheel bearing flange 20 extends and behind the bending edge 26 of the first section 23 ends. The groove 29 preferably ends before the transition area 31 , The groove 29 has at least one radius R. Preferably, the groove 29 have multiple radii, which can achieve a better stress distribution.

The groove 29 has a groove depth 33 on, which at most the material thickness of the slinger 22 equivalent. It is also conceivable, however, that the groove depth 33 at the most corresponds to the overlap of an interference fit. With reference number 34 is the area of the first section 23 of the pressed-on centrifugal plate 22 referred to, up to the groove 29 extends. The area 34 forms the static seat of the first section 23 of the slinger 22 that is fitted on the receiving section 28 is arranged. The wheel flange edge of the groove 29 has a distance 35 to the bending edge 26 between the first section 23 and the intermediate section 24 on.

The intermediate section 24 forms a contact surface for a mounting tool with which the spin plate 22 on the wheel bearing flange 20 is pressed on. This is the spin plate 22 in the axial direction along the receiving portion 28 moves until the second section 25 at the plant section 30 is applied. Due to the bending elasticity of the slinger 22 the skid plate springs 22 at the bending edge 26 , which is the area of highest stiffness of the slinger 22 represents, radially in the groove 29 on. The spin plate 22 is by means of fitting on the receiving section 28 held strong. The by overpressure in the groove 29 spring-loaded bending edge 26 secures the skid plate 22 against an axial Wandem in the direction of the rolling elements due to micro-vibrations, as by the micro-vibrations in the spin plate 22 introduced forces the surface pressure generated by the overpressure of the bending edge 26 have to overcome. Thus, by the compression in the groove 29 achieves a comparable holding effect, as in an end-side support of the first section 23 at a radial, circumferential step on the receiving portion 28 , as provided by the prior art. Unlike this, however, assembly problems resulting from the presence of the stage are avoided.

In 3 is a schematic representation of a second embodiment of a wheel bearing assembly according to the invention shown. For corresponding elements of the wheel bearing assembly, the same reference numerals are used. The second embodiment differs from the first embodiment in that an additional groove 36 in the area of the bending edge 27 between the intermediate section 24 and the second section 25 of the slinger 22 is provided. This will overpressure the slinger 22 favored in the axial direction, whereby the flat concerns of the second section 25 at the plant section 30 of the wheel bearing flange 20 is ensured at the end of the assembly process. The bending edge 27 springs when pressing the slinger 22 also on, and remains in this Overpriced position. As a result, a flat resting of the second section 25 at the plant section 30 reached and held.

The representation in 4 shows a schematic representation of a third embodiment of a wheel bearing assembly according to the invention. Again, the same reference numerals are used for corresponding elements of the wheel bearing assembly. In the 4 illustrated third embodiment differs from the second embodiment in that on the receiving portion 28 a, in particular circumferential, projection 37 is provided, on which the first section 23 of the slinger 22 latched in pressed position. In this case, the problem known from the prior art that the first section is not locked during pressing, by the overpressure in the areas of the two bending edges 26 . 27 prevented. The overpressure in the first groove 29 make sure the first section 23 when pressing through the mounting tool complete over the projection 37 is moved away. Thus, the first section 23 at the latest when moving out of the assembly tool on the projection 37 lock.

LIST OF REFERENCE NUMBERS

1

Wheel bearings

2

wheel bearing seal

3

splash plate

4

seal set

5

Torsion-resistant bearing part

6

rolling elements

7

Rotatable bearing part

8th

wheel bearing flange

9

Inner radius of the bearing part 7

10

support zone

11

attachment section

12

contour

13

cavity

14

step

15

piston rod

16

actuating piston

17

actuating piston

18

bore

19

bore

20

wheel bearing flange

21

Rotatable bearing part

22

splash plate

23

first section

24

intermediate section

25

second part

26

bending edge

27

bending edge

28

receiving portion

29

groove

30

contact section

31

Transition area

32

cavity

33

groove depth

34

Area

35

distance

36

groove

37

head Start

Claims (10)

Wheel bearing arrangement comprising a wheel bearing designed as an angular contact ball bearing or tapered roller bearing which comprises rolling elements guided between a torsionally rigid bearing part and a rotatable bearing part connected to a wheel bearing flange, wherein the wheel bearing flange (20) faces the wheel bearing, with a radially extending contact section (30) is, and the rotatable bearing part (21) has a Wälzkörperlaufbahn, in which in the direction of the Radlagerflansches (20) an axially extending, a spin plate (22) receiving receiving portion (28) adjacent, wherein the spin plate (22) a first, itself a substantially axially extending portion (23) and a second, substantially radially extending portion (25) which are at an angle to each other, wherein the first portion (23) and the second portion (24) in each case by a bending edge ( 26, 27) are connected to an intermediate portion (24), characterized gekennzeic hnet that in the receiving portion (28) has a radial circumferentially formed groove (29) is arranged, which extends in the axial direction in sections below the first portion (23) of the spin plate (22) and in the direction of Radlagerflansches (20) behind the Bending edge (26) of the first section (23) ends. Wheel bearing arrangement according to Claim 1 , characterized in that the groove (29) in the receiving portion (28) has one or more radii (R). Wheel bearing arrangement according to one of the preceding claims, characterized in that the groove (29) in the receiving portion (28) has a groove depth (33) which corresponds to the material thickness of the slinger (33). Wheel bearing arrangement according to one of the preceding claims, characterized in that the groove (29) in the receiving portion (28) has a groove depth (33) which corresponds to the overlap of an interference fit. Wheel bearing arrangement according to one of the preceding claims, characterized in that the groove (29) in the receiving portion (28) has a groove depth (33) which corresponds to the material thickness of the slinger (33) and the overlap of an interference fit. Wheel bearing arrangement according to one of the preceding claims, characterized in that on the abutment portion (30) a further groove (36) is arranged, which extends in sections below the second portion (25) of the spin plate (22) and in the direction of the receiving portion (28). seen behind the bending edge (27) of the second section (25) ends. Wheel bearing arrangement according to one of the preceding claims, characterized in that the first portion (23) of the centrifugal plate (22) for axial securing on a projection (37) is supported. Wheel bearing arrangement according to one of the preceding claims, characterized in that the intermediate portion (24) of the centrifugal plate (22) is designed as a contact surface intended for a mounting tool. Wheel bearing arrangement according to one of the preceding claims, characterized in that adjoining the second portion (25) of the centrifugal plate (22) is a further profiled section which extends in sections in the direction of the torsionally rigid bearing part. Wheel bearing arrangement according to one of the preceding claims, characterized in that a sealing means is arranged in a cavity (13) forming between the wheel bearing flange (8) and the splash plate (22).

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