DE102024200305A1 - arrangement of a wheel carrier and a constant velocity joint - Google Patents

Abstract

An arrangement comprising a wheel carrier (30) and a constant velocity joint (40) with a joint seal (70) sealing the constant velocity joint (40), has a corrosion-protected sealing ring (50) which is fixed to the constant velocity joint (40), in cooperation with the wheel carrier (30) provides a contact-free pre-seal for a wheel bearing (20) and covers the outer circumference of the constant velocity joint (40) from the pre-seal to the joint seal (70).

Description

The invention relates to an arrangement comprising a wheel carrier and a constant velocity joint with a joint seal sealing the constant velocity joint.

Such arrangements are used on driven axles of motor vehicles, whereby the wheel carrier, also known as a pivot bearing on front axles, serves to rotatably mount a vehicle wheel and to support it against a vehicle body via wheel guide members, while the constant velocity joint is usually part of a drive shaft via which the vehicle wheel is driven.

To allow the vehicle wheel to be rotatably supported, a wheel bearing is arranged on the wheel carrier, which must be protected against the ingress of moisture and dirt. For this purpose, appropriate sealing devices can be provided directly on the wheel bearing itself. In order to reduce the associated effort on the wheel bearing and to minimize friction effects, it is also known to use a pre-seal to reduce the penetration of moisture and dirt to the wheel bearing. Such pre-seals can in particular be designed to be contact-free.

A generic arrangement of the type mentioned above is DE 10 2015 211 455 B4 A spacer element is proposed as a pre-seal, which is arranged in the power flow between a wheel bearing and a drive shaft. The spacer element has a radial disk, the outer edge of which forms a narrow gap to the wheel carrier, which is intended to prevent moisture and dirt from penetrating the wheel bearing. Another sealing concept with a labyrinth-like pre-seal is from WO 2010/018041 A1 known.

In arrangements of the type mentioned above, not only the wheel bearing but also the constant velocity joint must be protected. For this purpose, a corresponding seal is provided on the constant velocity joint, which prevents moisture and dirt from penetrating the constant velocity joint. Bellows (also known as rolling bellows) and/or metal caps are usually used to seal the opening side of the constant velocity joint. Such a bellows or metal cap is mounted on the outer circumference of the constant velocity joint. However, they only overlap a partial area, so that the rest of the outer circumference up to the wheel carrier remains exposed to moisture and dirt. To prevent corrosion in this area of the outer circumference of the constant velocity joint, the constant velocity joint is coated with paint.

To ensure that the paint adheres sufficiently to the surface, the component in question must first be cleaned before painting and then coated with an adhesion promoter. These work steps are often carried out in specialised companies, which creates costs for handling the components and transporting them. The application of coatings and paintwork also involves energy consumption and complex environmental protection measures. Long production lead times also lead to high capital commitment.

The present invention is based on the object of remedying this situation. In particular, it aims to reduce the manufacturing costs of an arrangement of the type mentioned at the outset.

This object is achieved by an arrangement comprising a wheel carrier and a constant velocity joint with a joint seal sealing the constant velocity joint according to patent claim 1, which is characterized in that a corrosion-protected sealing ring is fixed to the constant velocity joint, which in cooperation with the wheel carrier provides a contact-free pre-seal for a wheel bearing and which covers the outer circumference of the constant velocity joint from the pre-seal to the joint seal.

By integrating the corrosion protection for the outer circumference of the constant velocity joint into the sealing ring for the pre-seal, the time-consuming external painting of the constant velocity joint can be eliminated. This results in a significant simplification of the manufacturing effort and associated processes.

Particular embodiments of the invention are the subject of further patent claims.

For example, the sealing ring can be made of a corrosion-resistant material. In addition to corrosion-resistant metal alloys, plastics and fiber composite materials are also suitable.

In order to facilitate production, the sealing ring can in particular be a sheet metal ring.

Alternatively or additionally, the sealing ring can have a corrosion-resistant coating on its outside.

There are already very economical automated processes for applying corrosion protection to sheet metal rings.

Sheet metal rings, for example, can be produced cost-effectively in large quantities as deep-drawn parts from a sheet metal blank.

According to another special embodiment of the invention, the sealing ring on the side of the joint seal is overlapped by the joint seal radially on the outside. This avoids a visible end edge on the sealing ring. In addition, a joint seal resting on the sealing ring can prevent moisture from penetrating under the sealing ring.

However, a reverse arrangement is also possible, namely that the sealing ring on the side of the joint seal overlaps the joint seal radially on the outside. In this case, the end edge of the sealing ring remains exposed. However, this can be pressed against the joint seal if necessary in order to also seal or even to fix the joint seal or at least to support its fixation to the constant velocity joint.

The joint seal can in particular comprise a bellows and/or a sheet metal cap which overlaps with the sealing ring. In a variation of this, the sealing ring and the joint seal can also sit axially butt-to-butt on the outer circumference of the constant velocity joint.

According to another particular embodiment of the invention, the sealing ring has a sleeve section with a diameter jump and preferably a transition slope >30° between the diameter jump. This improves the rigidity of the sealing ring, which means that it can be made from thin material and thus very lightweight.

It is also possible to provide a radially protruding projection on the sealing ring for the engagement of an assembly tool. This can facilitate particularly automated cardan shaft assembly.

The sealing ring can be secured to the constant velocity joint in different ways. A particularly simple variant is that the sealing ring has a fastening section that is secured with a press fit on the outer circumference of an outer joint part of the constant velocity joint. Alternatively or additionally, the sealing ring can be secured by the joint seal.

According to another special embodiment of the invention, the sealing ring is fixed at least axially by the joint seal. The fixation can take place in one axial direction in the sense of a stop or in both axial directions in the sense of an axial fixation on both sides.

According to a further special embodiment of the invention, the sealing ring can be supported axially with its edge facing the joint seal against a contact shoulder formed on the constant velocity joint. A defined axial position of the sealing ring can be specified via the contact shoulder.

According to another particular embodiment of the invention, the sealing ring for providing the pre-seal can have a pre-seal section which forms a sealing gap with the wheel carrier with two or more changes of direction. This creates very effective protection against the penetration of moisture and dirt to the wheel bearing.

The configuration according to the invention combines protection of the wheel bearing against moisture and dirt with effective corrosion protection of the constant velocity joint. In conjunction with a wheel carrier made of a corrosion-resistant material, such as an aluminum alloy, a high-quality appearance is also achieved by avoiding rust spots in the visible area.

Furthermore, a bead for fixing the joint seal can be formed, namely either only on the outer circumference of the constant velocity joint, or together partly by the constant velocity joint and partly by the sealing ring, or only on the outer circumference of the sealing ring.

• 1 eine Längsschnittansicht einer Anordnung aus einem Radträger und einem Gleichlaufgelenk nach einem ersten Ausführungsbeispiel der Erfindung,
• 2 eine Längsschnittansicht einer Anordnung aus einem Radträger und einem Gleichlaufgelenk nach einem zweiten Ausführungsbeispiel der Erfindung,
• 3 eine Längsschnittansicht einer Anordnung aus einem Radträger und einem Gleichlaufgelenk nach einem dritten Ausführungsbeispiel der Erfindung,
• 4 eine Variante für die Anbindung eines Faltenbalgs einer Gelenkdichtung,
• 5 eine weitere Variante für die Anbindung einer Blechkappe einer Gelenkdichtung,
• 6 weitere Variante für die Anbindung einer Gelenkdichtung,
• 7 eine Längsschnittansicht einer Anordnung aus einem Radträger und einem Gleichlaufgelenk nach einem vierten Ausführungsbeispiel der Erfindung,
• 8 eine Längsschnittansicht einer Anordnung aus einem Radträger und einem Gleichlaufgelenk nach einem fünften Ausführungsbeispiel der Erfindung,
• 9 eine Längsschnittansicht einer Anordnung aus einem Radträger und einem Gleichlaufgelenk nach einem sechsten Ausführungsbeispiel der Erfindung,
• 10 eine Detailschnittansicht einer Variante des Dichtrings,
• 11 eine Detailschnittansicht einer Variante des Dichtrings,
• 12 eine Detailschnittansicht einer Variante des Dichtrings,
• 13 eine Detailschnittansicht einer Variante des Dichtrings,
• 14 eine Detailansicht der Einbausituation einer Anordnung aus einem Radträger und einem Gleichlaufgelenk nach einem weiteren Ausführungsbeispiel der Erfindung,
• 15 eine Detailansicht der Einbausituation einer Anordnung aus einem Radträger und einem Gleichlaufgelenk nach einem weiteren Ausführungsbeispiel der Erfindung, und in
• 16 eine Detailansicht der Einbausituation einer Anordnung aus einem Radträger und einem Gleichlaufgelenk nach einem weiteren Ausführungsbeispiel der Erfindung.

In the following, ways of implementing the invention are explained in more detail using embodiments shown in the drawing. The drawing shows:

• 1 a longitudinal sectional view of an arrangement of a wheel carrier and a constant velocity joint according to a first embodiment of the invention,
• 2 a longitudinal sectional view of an arrangement of a wheel carrier and a constant velocity joint according to a second embodiment of the invention,
• 3 a longitudinal sectional view of an arrangement of a wheel carrier and a constant velocity joint according to a third embodiment of the invention,
• 4 a variant for the connection of a bellows of a joint seal,
• 5 another variant for the connection of a sheet metal cap of a joint seal,
• 6 another variant for the connection of a joint seal,
• 7 a longitudinal sectional view of an arrangement of a wheel carrier and a constant velocity joint according to a fourth embodiment of the invention,
• 8 a longitudinal sectional view of an arrangement of a wheel carrier and a constant velocity joint according to a fifth embodiment of the invention,
• 9 a longitudinal sectional view of an arrangement of a wheel carrier and a constant velocity joint according to a sixth embodiment of the invention,
• 10 a detailed sectional view of a variant of the sealing ring,
• 11 a detailed sectional view of a variant of the sealing ring,
• 12 a detailed sectional view of a variant of the sealing ring,
• 13 a detailed sectional view of a variant of the sealing ring,
• 14 a detailed view of the installation situation of an arrangement of a wheel carrier and a constant velocity joint according to a further embodiment of the invention,
• 15 a detailed view of the installation situation of an arrangement of a wheel carrier and a constant velocity joint according to a further embodiment of the invention, and in
• 16 a detailed view of the installation situation of an arrangement comprising a wheel carrier and a constant velocity joint according to a further embodiment of the invention.

The embodiments explained in more detail below each show a wheel hub 10, a wheel bearing 20 and a wheel carrier 30 which is mounted on the wheel hub 10 via the wheel bearing 20.

Furthermore, a constant velocity joint 40 of a drive shaft is provided, which is coupled to the wheel hub 10 for torque transmission. A joint seal 70 is arranged on the constant velocity joint 40, which seals the constant velocity joint 40 against the ingress of dirt and moisture.

Furthermore, a sealing ring 50 is fixed to the constant velocity joint 40, which on the one hand, in cooperation with the wheel carrier 30, provides a contact-free pre-seal for the wheel bearing 20 and on the other hand covers the outer circumference of the constant velocity joint 40 from the pre-seal to the joint seal 70. The surface of the constant velocity joint 40 is therefore not visible.

The sealing ring 50 is also protected against corrosion, either because it is made of a corrosion-resistant material or because it has a corrosion-resistant coating on the outside.

1 shows a longitudinal sectional view of an arrangement of a wheel carrier 30 and a constant velocity joint 40 according to a first embodiment.

In 1 the wheel bearing 20 has, for example, a wheel bearing outer ring 21 which is fixed to the wheel carrier 30. The wheel bearing outer ring 21 is preferably rotatably mounted on the wheel hub 10 via two roller bearings 22 and 23 of the wheel bearing. In addition, the wheel bearing 10 can have dedicated wheel bearing seals 24 and 25 which seal the roller bearings 22 and 23 from the outside. The wheel bearing seals 24 and 25 are arranged in an area between the wheel bearing inner ring 21 and the wheel hub 10. The said non-contact pre-seal, which is provided by the sealing ring 50 and the wheel carrier 30, is arranged at a distance from the rolling bearings 22 and 23 and is located between the constant velocity joint 40 and the wheel carrier 30. Due to the pre-seal by the sealing ring 50, the dedicated wheel bearing seals 24 and 25 can be designed to be particularly low-friction.

The rolling bearings 22 and 23 can be designed as complete bearings, each with its own inner bearing ring and its own outer bearing ring, as well as rolling elements arranged between them. However, it is also possible to integrate individual bearing rings into a common wheel bearing outer ring 21 and/or into the wheel hub 10.

In 1 For example, the bearing outer rings of the rolling bearings 22 and 23 are combined to form a common wheel bearing outer ring 21, which also forms support and fastening structures 26 for connection to the wheel carrier 30.

For the 1 For the left and thus joint-remote rolling bearing 22, the bearing inner ring is integrated into the wheel hub 10, whereas for the 1 right and thus joint-close rolling bearing 23, the bearing inner ring 29 is designed as an independent component. This bearing inner ring 29 can also be understood below as a component or part of the wheel hub 10.

If they are available as separate bearing rings, they are axially fixed and supported on the wheel bearing outer ring 21 or the wheel hub 10 using suitable axial securing means such as contact shoulders, axial securing rings, receiving grooves or the like. The bearing inner ring 29 can be formed, for example, by forming an end section of the wheel hub 10 to the wheel hub 10. This can be done, for example, by orbital forging or orbital pressing.

The wheel hub 10 is connected in a rotationally fixed manner to an outer joint part 49 of the constant velocity joint 40. In the embodiment according to 1 For this purpose, a planar spline arrangement 11/41 is shown as an example, which forms the interface between the constant velocity joint 40 and the wheel hub 10. For this purpose, a planar spline 11 or 41 is formed on opposite end walls of the constant velocity joint 40 and the wheel hub 10. The teeth of these two planar spline arrangements 11 and 41 are in mesh with one another. In the present case, planar spline is understood to mean a front-side radial toothing structure on a component, which can be coupled to a corresponding front-side radial toothing structure on another component for the purpose of torque transmission. The tooth engagement is free of play and suitable for transmitting high torques. Such planar spline arrangements are occasionally also referred to as Hirth or spur gear arrangements.

A clamping device 60, preferably in the form of a clamping bolt, can be provided to hold the two planar splines 11 and 41 on the wheel hub 10 and on the constant velocity joint 40 axially in engagement with one another when it is in the clamped state.

The clamping device 60 preferably extends centrally through the two planar splines 11 and 41. In particular, the clamping device 60, or the clamping bolt, can be supported on the wheel hub 10 with a head 61 and can be screwed to the constant velocity joint 40 via a thread 62. Installation in the opposite direction is also possible.

Optionally, a sealing sleeve 80 can also be provided, which serves to surround and seal the planar spline arrangement 11/41 radially on the outside and thus protect it against corrosion. For this purpose, the sealing sleeve 80 can be clamped axially between the wheel hub 10 and the constant velocity joint 40, for example. In particular, the sealing sleeve 80 can have an end face 81, which in the assembled state is pressed against an opposite end wall 12 of the wheel hub 10. In the present case, 1 the bearing inner ring 29 of the right rolling bearing 23 is considered to be part of the wheel hub 10. However, support directly against a wall section of the wheel hub 10 is also possible. It is also possible to fix the sealing sleeve 80 to the components mentioned in another way, for example by locking, pressing, gluing or the like.

The sealing sleeve 80 can be pre-assembled on the constant velocity joint 40 such that, in the assembled state of the arrangement, it engages with the wheel hub 10 outside the force flow of the wheel bearing 20.

Optionally, as for example in 7 and 8 As indicated, the sealing sleeve 80 together with the sealing ring 50 form a component, in particular it is manufactured in one piece. It is also possible to initially manufacture the sealing sleeve 80 and the sealing ring 50 separately and to connect them to one another before assembly on the constant velocity joint 40.

The sealing sleeve 80 can have a sleeve-shaped sealing section 81 which radially surrounds the planar spline arrangement 11/41 in the manner of a sleeve and rests, for example, on corresponding outer circumferential sections of the wheel hub 10 and the constant velocity joint 40. A first end face 82 of the sealing sleeve 80 rests against an end wall 12 of the wheel hub 10, here the bearing inner ring 29 of the 1 right rolling bearing 23, and an opposite second end face 83 against a wall shoulder 42 of the constant velocity joint 40. The sealing function with regard to the planar spline arrangement 11/41 can be carried out on the end faces 82, 83 and/or to the outer circumferential sections of the wheel hub 10 and the constant velocity joint 40. If the sealing is carried out against the outer circumferential sections of the wheel hub 10 and the constant velocity joint 40, axial support of the end faces 82 and/or 83 can be dispensed with if necessary. A circumferential web 84 can protrude radially from the sleeve-shaped sealing section 81 if necessary, for example to stiffen the sleeve-shaped sealing section 81 and/or to enlarge the axial support base on the constant velocity joint 40 for assembly.

The contact-free pre-seal for the wheel bearing 20 is 1 by the sealing ring 50 and a corresponding counter contour on the wheel carrier 30 by forming a narrow gap between them, which inhibits the entry of water and dirt.

In the simplest case, the sealing ring 50 is designed in the form of a sleeve which is fixed to the constant velocity joint 40 with a first end section 50a and forms a gap with the wheel carrier 30 with a further end section 50b.

In the 1 In the first embodiment shown, the sealing ring 50 has a sleeve portion 51 with a diameter jump 52 and a transition bevel 53 with a bevel angle of preferably more than 30° between the diameter jump 52. The transition bevel 53 connects two sleeve sections 51a and 51b with different diameters.

The sealing ring 50 can be made of plastic or fiber composite material. Furthermore, the sealing ring can be a sheet metal ring 50. In particular, the sealing ring 50 can be made as a deep-drawn part from a sheet metal plate.

The joint-side end portion 50a of the sealing ring 50 axially adjoins the joint seal 70, so that the outer circumference of the constant velocity joint 40, in particular the outer joint part 49 thereof, is covered.

The sealing ring 50 and the joint seal 70 can be overlapped, as will be explained in more detail below.

To secure it to the constant velocity joint 40, at least the joint-side end section 50a of the sealing ring 50 can be pressed with a wall section 44 on the outer circumference of the outer joint part of the constant velocity joint 40. However, fastening can also be carried out in another way, as will be explained in more detail below.

Furthermore, the sealing ring 50 can have a radially encircling projection. This can be designed, for example, as a circumferential web 54, which protrudes radially from the sleeve section 51, for example at the wheel bearing-side end section 50b. It can be used for engaging an assembly tool. For an assembly tool, a web in the more accessible area of the outer joint part of the constant velocity joint 40, in the sectional view shown in the figures above the outer joint part or its joint bell, namely in the direction of the vehicle interior, would be even more practical. This is shown in 13 shown as an example at the reference numerals 51c and 56.

The projection or web 54 - as a pre-sealing section on the sealing ring 50 - forms with corresponding wall sections on the wheel carrier 30 the said narrow gap, which inhibits the entry of moisture and dirt and thus acts as a pre-seal for the wheel bearing 20 and its wheel bearing seal 25.

For the corresponding wall sections on the wheel carrier 30, a radially inwardly directed projection 31 can be formed or attached to the wheel carrier 30, which has an axial annular wall 32 parallel to the projection or web 54. In the longitudinal section profile of the sealing ring 50 according to 1 This results in a gap path running radially to the axis of rotation A of the wheel hub 10, the extent of which in the radial direction is significantly greater than an axial gap path on the outside of the seal in the axial direction, namely parallel to the axis of rotation A, between the radial outer edge 55 of the web 54 and the wheel carrier 30.

An additional axial gap path on the inside of the seal can be provided between a radial inner edge 33 of the projection 31 of the wheel carrier 30 and the constant velocity joint 40, as shown in 1 is shown.

Since the projection 31 is located on the wheel carrier 30, the projection 31 can be designed relatively freely. In particular, it is possible to form the projection 31 integrally with the wheel carrier 30. However, it is also possible to attach a corresponding ring for the projection 31 to the wheel carrier 30 in order to create even more complex sealing gap configurations or labyrinths if necessary.

An alternative design of the sealing ring 50 is shown by way of example in 2 which, incidentally, 1 Compared to 1 also in 1 optional web 54, so that the sealing ring 50 consists only of a sleeve section 51 with a diameter jump 52 and a transition bevel 53 in between.

In contrast to the first embodiment in 1 can be in the second embodiment in 2 the diameter jump 52 can be designed in reverse, so that the diameter decreases from the wheel bearing side sleeve section 51b to the joint side sleeve section 51a.

Finally, in 2 the axial gap path along the wheel bearing side sleeve section 51b is greater than the radial gap path at its front edge.

3 shows as a third embodiment a further modification of the first embodiment, whereby only the differences will be discussed below. Compared to 1 In particular, the sealing ring 50 and the corresponding counter contour of the contact-free pre-seal on the wheel carrier 30 as well as the transition to the joint seal 70 are modified.

Compared to 1 the web 54 is again omitted, so that the sealing ring 50 consists only of a sleeve section 51 with a diameter jump 52 and a transition bevel 53 in between, the wheel bearing-side sleeve section 51b having a smaller diameter than the joint-side sleeve portion 51a.

To provide the pre-seal, the wheel bearing-side sleeve section 51b extends into an annular groove 34 on the wheel carrier 30, which can be formed, for example, on the projection 31 of the wheel carrier 30. The annular groove 34 and the wheel bearing-side sleeve section 51b are interlocked with one another without contact in order to achieve the longest possible gap path on the pre-seal within a compact space. In longitudinal section, this results in two parallel axial gap paths along the wheel bearing-side sleeve section 51b, which are connected to form a C-profile by a significantly shorter radial gap path along the front end of the wheel bearing-side sleeve section 51b.

Compared to 1 In addition, the additional axial gap path on the inside of the seal between a radial inner edge 33 of the projection 31 of the wheel carrier 30 and the constant velocity joint 40 can be extended due to the inner edge 35 of the annular groove 34.

As in 1 the sealing ring 50 may have a fastening section which is fixed with a press fit on the outer circumference of the outer joint part 49 of the constant velocity joint 40. In 3 the wheel bearing-side sleeve section 51b is provided for this purpose. In addition, the sealing ring 50 on the side of the joint seal 70 can overlap the joint seal 70 radially on the outside. The overlap can be designed as a fastening and/or as a seal. If necessary, the wheel bearing-side sleeve section 51b can also be dispensed with in contact with the outer circumference of the outer joint part 49.

The 4 to 6 show various possibilities of interaction of the sealing ring 50 with the joint seal 70, which can be optionally combined with the aforementioned embodiments.

In 4 a joint seal 70 with a bellows 71 or rolling bellows is shown as an example. Bellows and rolling bellows can be fixed, for example, by hose clamps on the outside diameter of the outer joint part 49 of the constant velocity joint 40. The bellows 71 or rolling bellows overlaps the joint-side sleeve section 51a of the sealing ring 50 radially on the outside, so that the joint-side end edge of the sealing ring 50 is not visible. The overlap can also be designed as a fastening and/or as a seal. The wheel bearing-side sleeve section 51b can optionally be supported on the outer circumference of the outer joint part 49 of the constant velocity joint 40.

Instead of a bellows 71 or in addition to such a bellows, the joint seal 70 can have a sheet metal cap 72 which is fixed to the outer circumference of the outer joint part 49. This joint seal 70 seals the constant velocity joint 40 on its opening side so that no grease can escape and no dirt can enter the constant velocity joint 40. The sheet metal cap 72 can be pressed onto the outer diameter of the outer joint part 49 of the constant velocity joint 40 and crimped there. As in 5 As shown, the sheet metal cap 72 can overlap the sealing ring 50 radially on the outside and can optionally be placed against the sealing ring 50 in order to fix and/or seal the sealing ring 50.

In addition, the joint-side sleeve portion 51a of the sealing ring 50 can be supported on the outer circumference of the outer joint part 49 of the constant velocity joint 40 and can also optionally be axially supported against a shoulder 45 on the outer joint part 49.

Instead of the sheet metal cap 72, the installation situation of the sealing ring 50 in 5 also a bellows 71 or rolling bellows analog 4 be used.

6 shows a sealing ring 50, which, with its joint-side sleeve section 51a, radially overlaps a sheet metal cap 72, or alternatively a bellows 71, on the outside. Here too, the overlap can be designed as a fastening and/or as a seal.

In addition, the wheel bearing-side sleeve portion 51b of the sealing ring 50 can be supported on the outer circumference of the outer joint part 49 of the constant velocity joint 40.

In the 7 and 8 Further embodiments of an arrangement on a wheel carrier 30 and a constant velocity joint 40 are shown in order to illustrate further, individually realizable modification features. On the one hand, the sealing ring 50 and the sealing sleeve 80 of the above examples are integrated into one component. On the other hand, the sealing ring 50 between the pre-seal and the joint seal 70 is slightly spaced from the outer circumference of the constant velocity joint.

The integrated component can be analogous to the 1 to 3 both a sleeve-shaped sealing section 81 of the sealing sleeve 80 for radial sealing of the planar spline arrangement 11/41 and a further sleeve-shaped sealing section, corresponding to the above sealing ring 50, for providing the contact-free pre-seal for the wheel bearing 20, wherein the further sleeve-shaped sealing section is connected to the first-mentioned sleeve-shaped sealing section 81 of the sealing sleeve 80 is connected by a radial web 54. In addition, the wheel carrier 30 has an annular groove 34, wherein a gap is formed as a sealing labyrinth between the first-mentioned sleeve-shaped sealing section 81 of the sealing sleeve 80, the further sleeve-shaped sealing section and the web 54 on the one hand and the annular groove 34 on the wheel carrier 30 on the other hand. Due to the long gap path through the sealing labyrinth, a particularly good effectiveness of the pre-seal is achieved here.

The integrated component 50/80 further comprises a third sleeve-shaped sealing section which protrudes axially from the second sealing section in the direction of the constant velocity joint 40 and sealingly abuts against the joint seal 70 of the constant velocity joint 40, as shown in the 7 and 8 is shown by way of example. This third sleeve-shaped sealing section corresponds to the joint-side sleeve section 51a of the sealing ring 50 already explained above, which adjoins the wheel bearing-side sleeve section 51b via a bevelled, possibly also stepped diameter jump, corresponding to the second sleeve-shaped sealing section of the integrated component 50/80.

The joint seal 70 of the constant velocity joint 40 can be, for example, a bellows 71, a rolling bellows, a sheet metal cap 72 with bellows or the like. It serves to seal the constant velocity joint 40 on its opening side so that no grease can escape or dirt can enter the constant velocity joint 40. Sheet metal caps 72 are usually pressed onto the outer circumference of the constant velocity joint 40 and crimped. Bellows 71 and rolling bellows can be attached to the outer circumference of the constant velocity joint 40 using hose clamps, clips or the like, for example.

Due to the contact between the sleeve-shaped third sealing section of the sealing ring 50 and the sealing element 70 of the constant velocity joint 40, the constant velocity joint 40 is completely covered on the outside, so that painting the outer surfaces of the constant velocity joint 40 to ensure a rust-free appearance is not necessary. The sealing ring 50 closes the gap between the sealing element 70 of the constant velocity joint 40 and the wheel hub 10 in a way that completely covers it.

In a further embodiment according to 9 can be modified from the 7 and 8 A small annular gap 73 should also be deliberately provided between the sealing ring 50 and the joint seal 70 of the constant velocity joint 40 so that incoming water can quickly escape again. The centrifugal force acting when the drive shaft is rotating can be used here. As in 9 As shown, the sealing ring 50 accordingly has a sleeve-shaped third sealing section which projects axially from the second sealing section in the direction of the constant velocity joint 40 and forms an annular gap 73 with the joint seal 70 of the constant velocity joint 40, such that any water entering can be drained away under centrifugal force. The annular gap 73 preferably has a gap width of only 1 to 3 mm.

The third sealing section in the 7 to 9 may further be designed such that it extends radially further outward than the furthest radially outward extension of an annular groove 34 for engagement with the sleeve-shaped second sealing portion in order to further impede the entry of water and dirt via the pre-seal.

The 10 to 13 show further possible modifications for the sealing ring 50, whereby only the profile shape is shown in each case. These modifications are applicable to all sealing rings 50 explained above.

9 illustrates a diameter jump 52 between two sleeve sections 51a and 51b. This is achieved by a transition bevel 53 which connects the two sleeve sections 51a and 51b. Preferably, the bevel angle at the transition bevel 53 is greater than 30°. The stepped design enables stiffening so that the sealing ring 50 can be made lightweight.

Instead of a transition slope 53, as in 10 shown, a right-angled step can also be provided. The sleeve sections 51a and 51b are connected in this case by a radial web 55.

Furthermore, as in the 12 and 13 shown, the sealing ring 50 has a radially projecting projection 56 for engagement with an assembly tool, for example to facilitate a cardan shaft assembly, in particular automatic cardan shaft assembly, in vehicle construction.

Such a projection 56 can be designed in the manner of a terminal radial web as described above in connection with the reference numerals 54 (cf. 12 ). However, it is also possible to arrange a projection 56 in a middle section 51c between the sleeve sections 51a and 51b, as shown in 13 shown.

The sealing ring 50 can optionally be provided with a component marking, for example by embossing, Burning in with a laser or paint application can be applied. The component marking can contain information on the part number, production date, production batches, production facilities and can be alphanumeric, with a data matrix code or barcode, for example.

The 14 to 16 finally show further possible modifications, among other things for the connection of the sealing ring 50 to the joint seal 70, which is shown here as an example with a bellows 71. This bellows 71 can be fixed with a clamp (not shown in detail) in the area of a joint opening 47 on an outer peripheral section 48 of the outer joint part 49 of the constant velocity joint 40.

The corrosion-protected sealing ring 50 has two sleeve sections 51a and 51b with a diameter jump 52 between them. While the wheel bearing-side sleeve section 51b engages in an annular groove 34 on the wheel carrier 30, the joint-side sleeve section 51a connects to the joint seal 70.

The sealing ring 50 can be molded to the outer contour of the outer joint part 49. In particular, the sealing ring 50 can be pressed onto the outer joint part 49 with one or both sleeve sections 51a and 51b.

In 14 the sealing ring 50 abuts on the joint side against a contact shoulder 45 of the outer joint part 48. The bellows 71 can end with the contact shoulder 45 or slightly overlap this and thus also the joint-side sleeve part sections 51a radially on the outside. In the latter case, a bead 90 for fixing the bellows 71 can be formed partly by the outer joint part 49 on the contact shoulder 45 and partly by the sealing ring 50.

15 shows a modification in which the bead 90 is arranged only on the outer joint part. A small annular gap can optionally be provided between the joint-side end edge of the sealing ring 50 and the joint seal 70. However, this is so narrow that the surface of the outer joint part 49 is not visible when viewed from an angle.

Finally, 16 the possibility of providing the bead 90 for fixing the bellows 71 entirely to the sealing ring 50.

Finally, it should be pointed out again that the coupling via the planar spline arrangement is optional in this case. Other connections are also possible at this point. In this sense, component 80 is optional in some design variants and can also be omitted, for example in configurations in which there is no planar spline arrangement to be protected.

The invention has been explained in more detail above using embodiments and further modifications. In particular, individual technical features which were explained above in the context of further individual features can be implemented independently of these and in combination with further individual features, even if this is not expressly described, as long as this is technically possible. The invention is therefore expressly not limited to the described embodiments and modifications, but encompasses all configurations defined by the patent claims.

list of reference symbols

10

wheel hub

11

first planar spline

12

bulkhead

20

wheel bearings

21

wheel bearing outer ring

22

rolling bearings

23

rolling bearings

24

wheel bearing seal

25

wheel bearing seal

26

support and fastening structure

29

bearing inner ring

30

wheel carrier

31

projection

32

axial ring wall

33

inner edge of the projection

34

annular groove of the projection

35

inner edge of the ring groove

40

constant velocity joint

41

second planar spline

42

wall ledge

43

threaded opening

44

Wall section on the outer circumference of the outer joint part

45

investment shoulder

47

joint opening

48

outer peripheral section

49

outer joint part

50

sealing ring

51

sleeve section

51a

sleeve section (joint side)

51b

sleeve section (wheel bearing side, non-joint side)

51c

radial web

51d

middle section

52

diameter jump

53

transition slope

54

web

55

radial outer edge

56

projection

60

clamping device

61

Head

62

thread/thread section

70

joint seal

71

bellows

72

sheet metal cap

80

sealing sleeve

81

sleeve-shaped sealing section

82

front side

83

front side

84

surrounding bridge

90

bead

A

axis

QUOTES INCLUDED IN THE DESCRIPTION

This list of documents listed by the applicant was 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 accepts no liability for any errors or omissions.

Cited patent literature

• DE 102015211455 B4 [0004]
• WO 2010/018041 A1 [0004]

Claims (15)

Arrangement comprising a wheel carrier (30) and a constant velocity joint (40) with a joint seal (70) sealing the constant velocity joint (40), characterized by a corrosion-protected sealing ring (50) which is fixed to the constant velocity joint (40), in cooperation with the wheel carrier (30) provides a contact-free pre-seal for a wheel bearing (20) and covers the outer circumference of the constant velocity joint (40) from the pre-seal to the joint seal (70). Arrangement of a wheel carrier (30) and a constant velocity joint (40) according to claim 1 , characterized in that the sealing ring (50) consists of a corrosion-resistant material. Arrangement of a wheel carrier (30) and a constant velocity joint (40) according to claim 1 or 2 , characterized in that the sealing ring (50) has a corrosion-resistant coating on its outside. Arrangement of a wheel carrier (30) and a constant velocity joint (40) according to one of the Claims 1 until 3 , characterized in that the sealing ring (50) is a sheet metal ring. Arrangement of a wheel carrier (30) and a constant velocity joint (40) according to one of the Claims 1 until 4 , characterized in that the sealing ring (50) is made as a deep-drawn part from a sheet metal plate. Arrangement of a wheel carrier (30) and a constant velocity joint (40) according to one of the Claims 1 until 5 , characterized in that the sealing ring (50) on the side of the joint seal (70) is overlapped radially on the outside by the latter. Arrangement of a wheel carrier (30) and a constant velocity joint (40) according to one of the Claims 1 until 5 , characterized in that the sealing ring (50) on the side of the joint seal (70) overlaps the joint seal (70) radially on the outside. Arrangement of a wheel carrier (30) and a constant velocity joint (40) according to one of the Claims 1 until 7 , characterized in that the joint seal (70) comprises a bellows (71) and/or a sheet metal cap (71) which is overlapped with the sealing ring (50). Arrangement of a wheel carrier (30) and a constant velocity joint (40) according to one of the Claims 1 until 8 , characterized in that the sealing ring (50) has a sleeve portion (51) with a diameter jump (52) and preferably a transition slope (53) >30° between the diameter jump (52). Arrangement of a wheel carrier (30) and a constant velocity joint (40) according to one of the Claims 1 until 9 , characterized in that the sealing ring (50) has a radially projecting projection (56) for engagement with an assembly tool. Arrangement of a wheel carrier (30) and a constant velocity joint (40) according to one of the Claims 1 until 10 , characterized in that the sealing ring (50) has a fastening portion which is fixed with a press fit on the outer circumference of an outer joint part (49) of the constant velocity joint (40). Arrangement of a wheel carrier (30) and a constant velocity joint (40) according to one of the Claims 1 until 11 , characterized in that the sealing ring (50) is axially fixed by the joint seal (70). Arrangement of a wheel carrier (30) and a constant velocity joint (40) according to one of the Claims 1 until 12 , characterized in that the sealing ring (50) is axially supported with its end edge facing the joint seal (70) against a contact shoulder (45) formed on the constant velocity joint (40). Arrangement of a wheel carrier (30) and a constant velocity joint (40) according to one of the Claims 1 until 13 , characterized in that the sealing ring (50) for providing the pre-seal has a pre-sealing section which forms a sealing gap with two or more changes of direction with the wheel carrier (30). Arrangement of a wheel carrier (30) and a constant velocity joint (40) according to one of the Claims 1 until 14 , characterized in that a bead (90) for fixing the joint seal (70) is formed either only on the outer circumference of the constant velocity joint (40), or jointly partly by the constant velocity joint (40) and partly by the sealing ring (50), or only on the outer circumference of the sealing ring (40).

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