DE102012021044A1 - Vehicle axle assembly with integrated pressure medium line for tire filling - Google Patents

Abstract

The invention relates to a vehicle axle assembly (10), comprising a hub (12) which is mounted rotatably about a central longitudinal axis (A) on a cylindrical axle body (14) and an axially inner and an axially outer shaft seal (36, 38) for the indirect or direct sealing between the axle body (14) and the hub (12). In order to enable an autonomous supply of pressure medium into a vehicle tire, the vehicle axle assembly (10) is characterized by an annular chamber (34) which is formed between the two shaft sealing rings (36, 38), the axle body (14) and the hub (12) a first pressure medium line (28) which extends through the axle body (14) or one of the two shaft sealing rings (36, 38) and opens into the annular chamber (34), and a second pressure medium line (40) extending from the annular Chamber (34) through the hub (12) and is designed for connection to a hub (12) mounted on the wheel.

Description

The present invention relates generally to the field of air-crafted vehicles, and more particularly to a vehicle axle assembly having an integrated pressure medium line for delivering a pressure medium to a tire.

For filling a vehicle tire with a pressure medium, usually compressed air, it is known to provide a valve on the vehicle wheel, via which the pressure medium can be introduced into the tire. In passenger cars, trucks or commercial vehicles such valves are usually arranged in the region of a rim on which the tire is mounted so that they are easily accessible to a person who wants to fill the tire. Typically, a vehicle-external pressure medium source is connected to the valve of the tire, usually by means of a hose, so as to control the tire pressure and correct if necessary.

This method of tire pressure regulation basically has the disadvantage that a regulation can be made only in places where a source of pressure medium is present, for. B. at gas stations, as in any case a coupling to a vehicle external pressure medium source is needed. In principle, it would be desirable to be able to autonomously carry out tire pressure regulation, for example, to adapt the tire pressure quickly to changed ambient temperatures during long-distance traffic.

It is therefore an object of the invention to provide a solution with which a Druckmittelzu- and -abfuhr can be made autonomously in a vehicle tire and preferably also while driving.

Starting from a Fahrzeugachsbrouppe with a hub which is rotatably mounted about a central longitudinal axis on a cylindrical axle body, and an axially inner and an axially outer shaft seal for direct or indirect seal between the axle and the hub, this object is achieved by an annular chamber, formed between the two shaft sealing rings, the axle body and the hub, a first pressure medium line which extends through the axle body or one of the two shaft seals and opens into the annular chamber, and a second pressure medium line extending from the annular chamber through the hub extends and is designed for connection to a wheel mounted on the hub.

Such an arrangement has the advantage that a supply of pressure medium from a vehicle-fixed part, namely the axle body, is made possible in the hub rotating relative to the axle body and thus into the wheel revolving around the axle body, without additional seals having to be provided for this purpose. This is achieved in that an annular chamber is provided between the two shaft sealing rings, which produces a suitable coupling for pressure medium transfer between the fixed axle body and the rotating wheel.

In order to form the annular chamber, according to the invention, a substantially hollow-cylindrical space is used between the axle body and the hub. The axially inner and the axially outer shaft seal are axially arranged at such a distance from each other that the annular chamber is formed.

The seal between the axle body and the hub by means of the shaft seals can be achieved directly or indirectly. In the case of an immediate seal, the shaft sealing ring is in direct contact both with the axle body and with the hub, so that a seal between the axle body and the hub is achieved solely by the shaft sealing ring. In an indirect sealing further elements are present between the shaft seal and the axle body or the hub, so that the shaft seal is not directly in contact with the axle body and / or the hub.

In the following, reference will first be made to directly sealing shaft seals. The case of indirectly sealing shaft seals will be explained later. In the case of directly sealing shaft sealing rings, the annular chamber is bounded by the lateral surface of the cylindrical axle body, the inner surface of the hub facing the lateral surface of the axle body and the two shaft sealing rings.

The first pressure medium line is provided to direct a pressure medium such as compressed air from an on-vehicle pressure medium source into the annular chamber. The pressure medium source can, for. B. be a compressor or a pressure fluid container in which, for example, compressed air is stored. The first pressure medium line is fixed relative to the axle body. It can be performed outside of the axle body and attached to this by means of suitable brackets. If the first pressure medium line is guided outside the axle body, it can preferably extend axially through one of the two shaft sealing rings in order to open into the annular chamber. It is also possible, at least in sections, to guide the first pressure medium line through the axle body, for example through a bore formed in the axle body. The first pressure medium line can then directly into the open annular chamber, ie without traversing one of the shaft seals.

The second pressure medium line serves to forward the pressure medium from the annular chamber and is designed at its chamber-distal end for connection to a wheel mounted on the hub. The second pressure medium line extends out of the annular chamber and can thereby extend at least in sections through the hub, for example through a bore in the hub. A wheel mounted on the hub may comprise a rim and a tire mounted on the rim with a valve for connecting the second pressure medium line. The second pressure medium line can thus be guided to the tire valve and connected to this, so that a pressure medium supply can be made in the tire. Advantageously, the tire valve can be designed as a Y-connection to allow a pressure medium supply either through the second pressure medium line or through another supply line, such as by an above-mentioned coupling to an external pressure medium source.

The two shaft sealing rings can be fixed to the hub, for example by frictional engagement, and slide upon rotation of the hub about the axle body on the lateral surface of the axle body. Likewise, both shaft seals may be fixed to the axle body and slide upon rotation of the hub about the axle body on the inner surface of the hub. If the first pressure medium line flows through one of the two shaft sealing rings into the annular chamber, the affected shaft sealing ring must be fixed relative to the axle body. If the first pressure medium line flows through the axle body into the annular chamber, the two shaft sealing rings can each be fixed in their own relative to the axle body or relative to the hub.

The axle assembly described is therefore particularly advantageous because in conventional axle assemblies, such as trucks, typically two abutting shaft seals are already present to ensure a seal of a wheel bearing between the axle and the hub. The shaft seals serve to prevent leakage of lubricant from the wheel bearing on the one hand and an entry of dust or dirt particles in the wheel bearing on the other hand. In the solution according to the invention, these already existing components are merely rearranged, d. H. axially spaced apart to form between the two shaft sealing rings a coupling space for the two pressure medium lines in the form of the annular chamber. Such a solution is also advantageous because, for example, in the case of a heavy goods vehicle or commercial vehicle, a pressure medium source in the form of an air compressor for the brake system is typically already present in the vehicle, which can be used to regulate the tire pressure.

When a supply of pressure medium through the first pressure medium line is formed in the annular chamber, an overpressure, d. H. a greater pressure than the atmospheric pressure, which seeks to axially expand the two shaft seals. To counteract an axial drift apart of the two shaft seals, at least one of the two shaft seals, but preferably both, may be provided adjacent to the annular chamber with a radial collar.

If a shaft seal is fixed to the hub, then such a collar will be formed radially inwardly on the shaft seal. If a shaft seal is fixed to the axle, then the collar will be formed on the shaft seal radially outward. In this case, the collar can be designed such that it already at normal pressure, d. H. at approximately atmospheric pressure, with the lateral surface of the axle body in contact. It is also conceivable that the collar at normal pressure from the lateral surface of the axle body is still spaced and elastically deformed only at an overpressure in the chamber so that it comes into contact with the lateral surface of the axle body. In both cases, the frictional force generated by the collar on the contacted surface leads to improved axial fixation of the respective shaft seal. Furthermore, an annular spring element can additionally be provided on the collar, whose spring force further reinforces the frictional force generated on the contacted surface.

The collar can also have a sealing lip, which is in contact with the axle body or the hub, at least in the case of an overpressure in the chamber. The sealing lip may be provided primarily for the purpose of effecting a further improved sealing of the annular chamber in addition to the fixing effect of the collar.

In order to counteract a possible divergence of the two shaft seals even more effective, may be present on the lateral surface of the axle relative to a radially inner collar of a shaft seal an annular groove into which the collar projects radially. Similarly, on the inner surface of the hub relative to a radially outer collar of a shaft seal, an annular groove may be present, in which the collar projects radially. At an overpressure in the chamber, the collar is then pressed against the groove wall and is supported on it, so that the shaft seal maintains its axial position.

An axial drift apart of the two shaft seals can also be countered be that on the lateral surface of the axle body, a circumferentially extending rib is present at which a radially inner collar of a shaft seal axially supported at least at an overpressure in the chamber. Similarly, on the inner surface of the hub there may be a circumferentially extending rib on which a radially outer collar of a shaft sealing ring is axially supported at least at an overpressure in the chamber.

Such a rib may be formed integrally with the axle body or the hub, but it may also be formed by an inserted into a groove snap ring or O-ring made of elastomeric material. According to one embodiment, the rib has a substantially rectangular cross-section.

Again, a radially inner collar may have a sealing lip which is in contact with the axle beam or rib at least at an overpressure in the chamber. Similarly, a radially outer collar may have a sealing lip which is in contact with the hub or rib at least at an overpressure in the chamber. Such a sealing lip can effect an improved sealing of the annular chamber in addition to the support function achieved by the cooperation of the collar and the rib.

According to another embodiment, an annular flange with two elastic, radial side walls is mounted between the two shaft sealing rings on the lateral surface of the axle body. The first pressure medium line can then open into the annular chamber in the annular flange between the two side walls. In such an arrangement, the sealing of the chamber can be effected in that the side walls of the annular flange elastically deformed at an overpressure in the chamber, d. H. pressed apart while being pressed axially against each one of the shaft seals.

In a further development of the aforementioned embodiment, a ring with U-shaped cross-section is fixed on the inner surface of the hub relative to the annular flange, the side walls are directed radially inwardly and engage over the elastic side walls of the annular flange. The second pressure medium line may then extend through the ring between its side walls into the hub. The sealing of the annular chamber can in this case take place in that the side walls of the annular flange elastically deform at an overpressure in the chamber and are pressed axially against each one of the side walls of the U-shaped ring.

The embodiment just described with a two elastic side walls having annular flange on the lateral surface of the axle body and attached to the inner surface of the hub ring with U-shaped cross-section or vice versa (U-shaped ring on the axle and ring flange on the hub) can also without the two shaft sealing rings are used, since the annular chamber is already fixed in this case by the interaction of the annular flange with the ring having the U-shaped cross-section.

An axial drift apart of the two shaft seals can also be prevented by the fact that the two shaft seals are axially rigidly coupled together. Such a rigid coupling can be achieved for example by attaching one or more rigid connecting elements between the two shaft sealing rings. Similarly, a drift apart of the two shaft sealing rings can be counteracted by the fact that the two shaft seals are axially elastically coupled together. An elastic coupling can be realized for example by attaching one or more spring elements between the two shaft sealing rings. The spring element or the spring elements can be designed so that they exert a drifting apart of the shaft sealing rings counteracting tensile force only when there is an overpressure in the annular chamber. A combination of rigid and elastic coupling of the two shaft seals is possible, for example, to allow a defined range of shaft seals a defined deformation in the axial direction.

According to a further embodiment, at least one of the two shaft sealing rings can be integrated in a ball bearing arranged between the axle body and the hub. In this case, the seal between the axle body and the hub is not achieved directly by the shaft seal, but only indirectly. Such a shaft seal is preferably arranged between the radially inner race and the radially outer race of the ball bearing so that it forms a sealing outer skin for the ball bearing in the area between the races, the penetration of dust and dirt particles in the ball bearing and an outlet of lubricants prevented from the ball bearing. The radially inner race of the ball bearing lies flat against the lateral surface of the axle body and is fixed relative to the axle body. The radially outer race of the ball bearing is applied flat against the inner surface of the hub and is fixed relative to the hub. The annular chamber is limited in this arrangement on its ball bearing side facing accordingly by the integrated shaft seal and the annular chamber facing side surfaces of the two races.

An axial drifting away of such a shaft seal at an overpressure in the chamber is usually prevented by the fixation of the ball bearing relative to the axle body and the hub. In addition, it is quite conceivable, analogous to the above-described shaft seals for such integrated shaft seals to provide a support structure, for. B. as a groove or rib on one of the races on which a respective collar can be supported at least at an overpressure in the annular chamber.

In principle, any desired combinations of indirectly and directly sealing shaft sealing rings are conceivable for the formation of the annular chamber. Thus, according to one embodiment, the annular chamber can be defined between an axially inner, directly sealing Welldichtring and an axially outer, indirectly sealing shaft seal. A reverse arrangement is conceivable, ie a limitation of the chamber by an axially inner, indirectly sealing Welldichtring and an axially outer, directly sealing shaft seal. Are in a Fahrzeugachsbroupp two spaced ball bearings with integrated shaft seals present, it is possible according to a further embodiment, the annular chamber between the two ball bearings, d. H. to form between two indirectly sealing shaft seals.

Finally, a valve for pressure relief of the annular chamber may be present. After the supply of pressure medium can thus be reduced overpressure in the annular chamber, in order to avoid that both the pressure medium lines and the annular chamber are permanently under high pressure.

According to a further aspect, the object mentioned at the outset is achieved by a vehicle axle assembly having a hub which is mounted rotatably about a central longitudinal axis on a cylindrical axle body. On an inner surface of the hub, a ring profile with U-shaped cross-section is present, the side walls extend axially or radially. Between the side walls a rotationally fixed with respect to the axle body sealing ring is arranged, which limits an annular chamber in the ring profile. A first pressure medium line extends through the sealing ring and opens into the annular chamber. A second pressure medium line extending out of the annular chamber through the annular profile and the hub is configured for connection to a wheel mounted on the hub.

This embodiment of the vehicle axle assembly makes it possible to form an annular chamber without the two shaft seals. Instead, the annular chamber is limited only by the annular profile connected to the inner surface of the hub and the sealing ring, which is arranged between the side walls of the annular profile.

The ring profile connected to the inner surface of the hub may be configured as a separate part which is fixed to the inner surface of the hub, but it may also be integrally formed with the hub, for example, cast together with the hub body, when the hub is a casting.

As with the Fahrzeugachsbroup described first arises at a pressure medium supply in the annular chamber, an overpressure, which here seeks to push the sealing ring axially out of the ring profile.

In order to counteract such pressing out of the sealing ring, a holder may be provided which fixes the axial position of the sealing ring at axially extending side walls of the annular profile and the radial position of the sealing ring at radially extending side walls of the annular profile. Such a holder can be realized, for example, as a stop on the first pressure medium line near the mouth of the same in the annular chamber to which the sealing ring is supported axially on axially extending side walls of the ring profile and radially extending side walls of the ring profile. Also, a support may be provided on the annular profile, for example in the form of a circumferential rib which is formed on the inside of a side wall or on both side walls of the annular profile. Furthermore, the sealing ring adjacent to the annular chamber at axially extending side walls of the annular profile radially inside and radially outside or at radially extending side walls of the ring profile axially inside and be provided axially outwardly with a collar, which at least at an overpressure in the chamber against the side walls of the annular profile is pressed and contributes by the resulting friction force in axially extending side walls to an axial fixation of the sealing ring or at radially extending side walls to a radial fixation of the sealing ring. In the case of axially extending side walls of the annular profile of the radially inner and the radially outer collar can also be positively supported axially in the annular chamber and in the case of radially extending side walls of the annular profile, the axially inner and the axially outer collar can be positively supported radially in the annular chamber For example, on a support structure which is present on the inside of the side walls of the ring profile. Such a support structure may be analogous to the vehicle axle assembly described first, z. B. as a groove or rib on which the respective collar can be supported at least at an overpressure in the annular chamber.

Several exemplary embodiments of a vehicle axle subassembly according to the invention are explained in more detail below with reference to the accompanying schematic drawings, in which:

1 a longitudinal sectional view of an embodiment of a vehicle axle according to the invention in an overview;

2 a part of the longitudinal sectional view of the vehicle axle assembly

1 in an enlarged view and with a modification for supplying a tire sealant;

3a and 3b a detailed view of an embodiment with two shaft sealing rings, both having a radially inner collar;

4a and 4b a detailed view of an embodiment with two shaft sealing rings, both of which have a radially inner collar with a spring element;

5a and 5b a detailed view of an embodiment with two shaft seals with radially inner collar and formed in the axle body annular grooves;

6a and 6b a detailed view of an embodiment with two shaft seals with radially inner collar and ribs formed on the axle body;

7a and 7b a detailed view of an embodiment with a shaft seal with radially inner collar and a shaft seal with radially outer collar;

8a and 8b a detailed view of an embodiment with a shaft seal with radially inner collar, a shaft seal with radially outer collar and associated, formed in the axle body and hub annular grooves;

9a and 9b a detailed view of an embodiment with a shaft seal with radially inner collar, a shaft seal with radially outer collar and associated, formed on axle and hub ribs;

10a and 10b a detailed view of an embodiment with an arranged between two shaft sealing rings on the axle ring flange;

11a and 11b a detailed view of an embodiment with an arranged between two shaft seals on the axle ring flange and a hub arranged on the U-shaped ring;

12a and 12b a detail view of an embodiment with two rigidly coupled shaft seals, each having a radially inner collar;

13a and 13b a detail view of an embodiment with two elastically coupled shaft seals, each having a radially inner collar;

14a and 14b a detailed view of an embodiment with two rigidly coupled shaft seals with radially inner collar and associated, formed on the axle body ribs;

15a and 15b a detailed view of an embodiment with two elastically coupled shaft seals with radially inner collar and associated, formed on the axle body ribs;

16a and 16b a detailed view of an embodiment with two elastically coupled shaft seals with radially inner collar and formed on the axle body flat ribs;

17a and 17b a detailed view of an embodiment with two rigidly coupled shaft seals and elastically coupled radially inner collar and formed on the axle body flat ribs;

18 a longitudinal sectional view of an embodiment of an axle assembly with a ball bearing, in which the axially outer shaft seal is integrated into the ball bearing;

19 a longitudinal sectional view of an embodiment of an axle assembly with two ball bearings, in which the axially outer shaft seal is integrated into the axially inner of the two ball bearings;

20 a longitudinal sectional view of an embodiment of an axle assembly with two ball bearings, in which both shaft seals are integrated in each one of the two ball bearings;

21a and 21b a detailed view of an embodiment with a U-shaped ring profile with axially extending side walls and a sealing ring arranged therein;

22a and 22b a detailed view of an embodiment with a U-shaped ring profile with axially extending side walls, a sealing ring arranged therein and ribs formed on the side walls;

23a and 23b a detailed view of an embodiment with a U-shaped ring profile with axially extending side walls, a sealing ring disposed therein and formed on the side walls flat ribs;

24a and 24b a detail view of an embodiment with a U-shaped ring profile with radially extending side walls, a sealing ring disposed therein and formed on the side walls flat ribs;

25a and 25b a detail view of an embodiment with a U-shaped ring profile with radially extending side walls, a sealing ring disposed therein and formed on the side walls flat ribs; and

26a and 26b show a detailed view of an embodiment with a U-shaped ring profile with radially extending side walls, a sealing ring arranged therein and formed on the side walls flat ribs.

In the following description of embodiments, like reference numerals are used to designate the same or equivalent elements.

1 shows in longitudinal section a Fahrzeugachsbrouppe 10 with a hub 12 which is rotatable about a central longitudinal axis A on a cylindrical, hollow axle body 14 is stored. In the illustrated embodiment, the storage of the hub 12 by two spaced along the axis A ball bearings 16 and 18 realized. The hub 12 is by means of screws 19 at one through the axle body 14 extending drive shaft 20 attached, which drives the drive generated by a motor, not shown, to the hub 12 transfers to the latter around the axle body 14 to turn. At the hub 12 are bolts 22 present at which a not shown here wheel can be placed and fixed by means of a rim on the hub. Further, at the wheel hub 12 one with her around the axle body 14 rotating brake disc 24 attached to by means of a vehicle-mounted brake 26 in a manner known to those skilled in the art at the hub 12 to be able to decelerate the attached vehicle wheel.

A first pressure medium line 28 is with a here only schematically illustrated, existing in the vehicle pressure medium source 30 connected, which may be, for example, a compressor for generating compressed air or a container with pressurized Reifenfüllmittel. In the embodiment shown, the first pressure medium line runs 28 from the pressure medium source 30 starting first outside the axle body 14 and then goes into a section 32 over, which is inside the axle body 14 is formed and in one between the axle body 14 and the hub 12 formed annular chamber 34 empties. The inside of the axle body 14 extending section 32 can as shown by a hole in the axle 14 be realized.

The annular chamber 34 is radially outward through the inner surface of the hub 12 , radially inward through the lateral surface of the axle body 14 and laterally by an axially inner shaft seal 36 and an axially outer shaft seal 38 limited and thus provides a direct through the shaft seals 36 and 38 sealed to the axle body 14 around the cavity. From the annular chamber 34 out runs a second pressure medium line 40 at the far end of the chamber to connect to one on the hub 12 attached wheel is configured. The second pressure medium line 40 runs in parts through the hub 12 through a hole in the hub 12 , And may be performed in their further course, for example, by a rim not shown here to a valve mounted on the rim tire. For example, the tire valve may be designed as a Y-connection to a pressure medium optionally through the second pressure medium line 40 or by another supply, z. B. from an external source of pressure medium to be able to feed into the tire.

For a better understanding of the further description, it should be pointed out that of the components described so far, only the axle body 14 and the first pressure medium line 28 as well as the pressure medium source 30 are fixed. Those components, however, directly or indirectly with the hub 12 connected, turn with the hub 12 around the axle body 14 as soon as the hub 12 through the drive shaft 20 is driven. So it turns in particular the second pressure medium line 40 , which in the course of the rotation over the annular chamber 34 or the sealed cavity formed by them, always fluid-conducting with the first pressure medium line 28 is coupled. Because this coupling is independent of the respective rotational position of the hub 12 is, a pressure medium supply or discharge not only at a standstill, but also while driving at a rotating hub 12 respectively. With the described arrangement, a tire pressure regulation can therefore be easily automated.

According to a development, the described arrangement of the axle assembly 10 not only for supplying a gaseous pressure medium such as compressed air, but also for supplying a liquid pressure medium For example, a tire sealant can be used. This can be advantageous, in particular in the event of a puncture. Such an embodiment requires only minor modifications of the in 1 shown axle assembly 10 in the area of the first pressure medium line 28 , This is exemplary in 2 shown where the first pressure medium line 28 at a branch point 42 branches and the branch then in a tire sealant-containing reservoir 44 is guided. From the reservoir 44 out leads a connection line 45 the tire sealant if necessary in the pressure medium line 28 into which the connecting line 45 at a union office 46 empties. In the illustrated embodiment is at the branch point 42 a switching mechanism 48 provided, which unlocks only one of the two lines, ie either the main line 28 or to the reservoir 44 leading branch. Will the switching mechanism 48 set to the branch, it will be in the reservoir 44 located tire sealant in the first pressure medium line 28 introduced and from there via the annular chamber 34 in the second pressure medium line 40 led to the tires. It is understood that this arrangement for initiating a tire sealant is merely exemplary. In principle, other arrangements are conceivable, by means of which a tire sealant in the pressure medium line 28 can be initiated, for example, by a manual docking.

In a further embodiment of the axle assembly 10 is a pressure relief device available. Since at a pressure medium supply both in the first and the second pressure medium line 28 and 40 as well as in the annular chamber 34 an overpressure of up to 10 or even 15 bar is generated, it makes sense to perform a pressure relief after completion of the pressure regulation, to prevent the pressure medium lines 28 and 40 and the chamber 34 constantly under pressure. The pressure relief device may be a relief valve, such as a mechanical or an electronically controlled valve located at a suitable location in the first pressure medium line 28 , the second pressure medium line 40 or in the area of the annular chamber 34 is arranged and can cause a controlled pressure relief.

With regard to the closer design of the annular chamber 34 as well as these axially laterally limiting shaft seals 36 and 38 will now be on the 3 to 17 referenced, which in each case by means of a detailed view in longitudinal section for the area of the annular chamber 34 illustrate different embodiments. In each case, the numbered with lower case letter "a" figure shows the state of the arrangement at atmospheric pressure and numbered lower case letter "b" the state of the same arrangement in one in the chamber 34 prevailing overpressure. Identical or equivalent elements are further designated by the same reference numerals as in the preceding figures, but the reference numerals for each of the following embodiments are supplemented with a separate lower case letter. Unless otherwise stated below, reference is made to the above explanations for the explanation of elements with reference numbers of the same number.

In the in the 3a and 3b shown embodiment are between the axle body 14a and the hub 12a an axially inner shaft seal 36a and an axially outer shaft seal 38a arranged. As shaft seals can be used commercially available oil seals, for example, so-called oil seals ^®. Both shaft seals 36a and 38a each stick radially outward by frictional engagement on the hub 12a and are each radially inward with a main sealing lip 50a respectively. 52 a provided by one of a hose spring 54a respectively. 56a generated contact force against the axle body 14a is pressed and thus an immediate seal between the axle body 14a and the hub 12a causes. With a rotation of the hub 12a around the axle body 14a the two oil seals rotate 36a and 38a due to the mentioned frictional engagement with the hub 12a with, leaving the main sealing lips 50a and 52a over the lateral surface 58a of the axle body 14a slide.

Both shaft seals 36a and 38a are also radially inward and adjacent to the annular chamber 34a each with a collar 60a respectively. 62a Mistake. Both collars 60a and 62a have a sealing lip 64a respectively. 66a on, both at least at an overpressure in the chamber 34a represented in 3b , with the lateral surface 58a of the axle body 14a in contact and in addition to the main sealing lips 50a respectively. 52a create a sealing effect. Im in 3a embodiment shown are the sealing lips 64a and 66a at normal pressure not in contact with the axle body 14a but only when there is an overpressure in the chamber 34a against the lateral surface 58a of the axle body 14a pressed. It is understood, however, that the collar 60a and 62a with the sealing lips 64a and 66a already at normal pressure with the axle body 14a can be in contact.

The at an overpressure in the chamber 34a generated contact pressure, which is the collar 60a and 62a with the sealing lips 64a and 66a on the lateral surface 58a of the axle body 14a presses, leaves the two shaft seals 36a and 38a stronger on the lateral surface 58a of the axle body 14a adhere, causing the shaft seals 36a and 38a can maintain their axial position longer. A force causing an overpressure in the chamber 34a an axial Disengagement of the two shaft seals 36a and 38a The effect is achieved by pressing the collar 60a respectively. 62a to the lateral surface 58a of the axle body 14a responds and an axial drift apart of the two wave rings 36a and 38a makes it much more difficult.

A development of this embodiment show the 4a and 4b , In contrast to the previous embodiment, here are the collar 60b and 62b additionally with an annular spring element 68b respectively. 70b provided whose spring force the above-mentioned contact force, which the collar 60b and 62b with the sealing lips 64b and 66b on the lateral surface 58b of the axle body 14b pushes, further strengthened. The spring elements 68b and 70b For this purpose, for example, be designed as a hose springs. Unlike in the previous embodiment, the collar 60b and 62b or the sealing lips 64b and 66b due to the spring elements 68b and 70b generated contact pressure already at a normal pressure in the chamber 34b with the lateral surface 58b of the axle body 14b in contact. However, it is also conceivable opposite the collar 60b and 62b or the sealing lips 64b and 66b on the lateral surface 58b of the axle body 14b to provide a circumferentially extending recess, so that by the spring elements 68b and 70b generated spring force is not quite enough to the collar 60b and 62b or the sealing lips 64b and 66b at normal pressure in the region of the recess against the axle body 14b to press. In this case, the collars would 60b and 62b or the sealing lips 64b and 66b the axle body 14b in the area of the recess only at an overpressure in the chamber 34b to contact.

As an axial drift apart of the two shaft seals 36 and 38 can be counteracted more effectively in the embodiment according to the 5a and 5b shown. This embodiment differs from that in the 3a and 3b example shown therein that the radially inner collar 60c and 62c the shaft seals 36c and 38c are formed radially inwardly longer, so that they are radially in on the lateral surface 58c of the axle body 14c existing annular grooves 72c respectively. 74c protrude. At an overpressure in the chamber 34c be the collar 60c and 62c against the lateral walls of the annular grooves 72c and 74c pressed like this in 5b is shown. An axial drift apart of the two shaft rings 36c and 38c is effectively prevented by this support. In addition, results from the contact of the collar 60c and 62c on the walls of the ring grooves 72c and 74c an additional seal of the annular chamber 34c ,

The 6a and 6b show another example, such as an axial drift apart of the two shaft seals 36 and 38 can be countered. The embodiment shown here differs from that in the 3a and 3b example shown therein that on the lateral surface 58d of the axle body 14d circumferentially extending ribs 76d and 78d are present, where the collar 60d and 62d at least at an overpressure in the chamber 34d support axially. Im in 6a embodiment shown are the collar 60d and 62d at normal pressure still from the ribs 76d and 78d spaced and come only at an overpressure with the ribs 76d and 78d in contact. It is understood, however, that even at normal pressure already a contact between the collar 60d respectively. 62d and the ribs 76d respectively. 78d can be present.

Another embodiment is in the 7a and 7b shown. This embodiment differs from the example in FIG 3a and 3b in that the inner shaft seal 36e by friction on the axle body 14e is held and therefore with respect to the axle body 14e is rotationally fixed. The shaft seal 36e is with a head seal lip 50e provided by one of a hose spring 54e generated contact force against the hub 12e is pressed and thus a seal between the axle body 14e and the hub 12e causes. With a rotation of the hub 12e around the axle body 14e is the shaft seal 36e relative to the axle body 14e stuck while with the hub 12e main sealing lip in contact 50e on the inner surface 80e the hub 12e slides.

The shaft seal is 36e is also adjacent to the annular chamber 34e radially outside with a collar 60e Mistake. The collar 60e has a sealing lip 64e on, at least at overpressure in the annular chamber 34e represented in 7b , with the inner surface 80e the hub 12e in contact and in addition to the sealing lip 50e creates a sealing effect. Im in 7a embodiment shown is the sealing lip 64e at normal pressure not yet in contact with the hub 12e but only when there is an overpressure in the chamber 34e against the inner surface 80e the hub 12e pressed. It is understood, however, that the collar 60e with the sealing lip 64e even at normal pressure in the chamber 34e with the hub 12e can be in contact.

Furthermore, this embodiment differs from the example according to the 3a and 3b in that the first pressure medium line 28e not here by a parallel to the axis A extending bore in the axle 14e is guided, but in the cavity between the hub 12e and the axle body 14e runs and passes through the inner shaft seal 36e extends to the annular chamber 34e to flow into. Here is one suitable holder 82e provided, which is the first pressure medium line 28e at the axle body 14e fixed.

In an analogous way, the differences in the 8a and 8b respectively. 9a and 9b shown embodiments of the embodiments of the 5a and 5b respectively. 6a and 6b ,

Another embodiment is in the 10a and 10b shown. This embodiment differs from the example in FIG 3a and 3b in that between the two shaft seals 36h and 38h on the lateral surface 58h of the axle body 14h an annular flange 84h with two elastic, radial sidewalls 86h and 88h is attached, wherein the first pressure medium line 28h in the ring flange 84h between the two side walls 86h and 88h into the annular chamber 34h empties. In this arrangement, the sealing of the chamber takes place 34h in that at least at an overpressure in the chamber 34h the side walls 86h and 88h of the annular flange 84h deform elastically, thereby being pushed apart and axially against each one of the shaft seals 36h and 38h be pressed. This situation is in 10b shown.

A modification of this embodiment is in the 11a and 11b illustrated. In addition to the previous example, here is on the inner surface 80i the hub 12i opposite the annular flange 84i a ring 90i fixed with U-shaped cross-section, whose side walls 92i and 94i directed radially inwardly and the elastic side walls 86i and 88i of the annular flange 84i spread. The second pressure medium line 40i extends between the side walls 92i and 94i through the ring 90i into the hub 12i , In this example, the elastic sidewalls 86i and 88i of the annular flange 84i at an overpressure in the chamber 34i not against the shaft seals 36i and 38i pressed, but against the side walls 92i and 94i of the ring 90i , This situation is in 11b illustrated. A seal of the annular chamber 34i So here is between the sidewalls 86i and 88i of the annular flange 84i and the side walls 92i and 94i of the ring 90i instead of. It is understood that in this case the shaft seals 36i and 38i with respect to the sealing of the annular chamber 34i are dispensable, since the annular chamber 34i already by the interaction of the annular flange 84i with the U-shaped cross-section ring 90i is defined.

The 12a and 12b show a development of the embodiment according to the 3a and 3b in which the two shaft seals 36j and 38j axially rigidly coupled together. In the illustrated embodiment is between the two shaft sealing rings 36j and 38j a circumferentially extending connecting element 96j attached, which are the two shaft seals 36j and 38j axially spaced apart holds. When the connecting element 96j extends continuously in the circumferential direction, it must have at least one opening, so that a pressure medium through the chamber 34j from the first pressure medium line 28j to the second pressure medium line 40j can get. Advantageously, instead of a continuous connecting element with one or more openings, a plurality of individual, mutually spaced connecting elements between the shaft sealing rings 36j and 38j be attached, for example, a number of individual webs or pins. It is understood that in such a configuration, an axial drift apart of the two shaft seals 36j and 38j is no longer possible.

Instead of a rigid coupling and an elastic coupling of the shaft seals may be provided. This is in the embodiment of 13a and 13b shown, which differs from the previous embodiment only in that instead of the rigid connecting element 96j a spring element 98k between the two shaft seals 36k and 38k is attached. The spring element 98k can be about, as shown, formed by a helical tension spring whose tensile force at an overpressure in the chamber 34k counteracts the resulting force, the two shaft seals 36k and 38k would like to squeeze in the axial direction. An axial drift apart of the two shaft seals 36k and 38k is locally restricted or prevented in this way and at a pressure relief in the chamber 34k take the two shaft seals 36k and 38k their original position again. It is understood that several spring elements between the two shaft seals 36k and 38k can be attached. It is also understood that other types of springs than a helical tension spring can be used.

Further embodiments result from any combination of the features of the embodiments described above. The 14a and 14b as well as the 15a and 15b show exemplarily two such combinations. In the 14a and 14b are the features of the embodiments of the 6a and 6b as well as the 12a and 12b combined. In 15a and 15b are the features of the embodiments of the 6a and 6b as well as the 13a and 13b combined.

The 16a and 16b show by way of example a variation of the embodiment of 15a and 15b , The difference here is that on the lateral surface 58n of the axle body 14n existing ribs 100n and 102n are designed as flat ribs. In this embodiment rely on a positive pressure in the chamber 34n the collar 60n and 62n not in the axial direction on the flat ribs 100n and 102n but off in the axial direction on the flat ribs 100n and 102n deferred, leaving the collar 60n and 62n or their sealing lips 64n and 66n radially on the flat ribs 100n and 102n be pressed. At a pressure relief, the two shaft seals 36n and 38n by the spring element 98n again axially from the flat ribs 100n and 102n pulled down. This embodiment is particularly advantageous when a pressure regulation is made while the vehicle is traveling. So they are at one in the chamber 34n existing overpressure occurring frictional forces between the sealing lips 64n and 66n and the flat ribs 100n and 102n significantly less than between the collar 60m and 62m and the ribs 76m and 78m according to the embodiment of the 15a and 15b ,

Another combination or variation possibility of the previous embodiments is through the 17a and 17b given. Here are the shaft seals 36o and 38o through a rigid connecting element 96o held axially fixed spaced from each other. In addition, a spring element 98o provided, which only in the area between the collar 60o and 62o is arranged. This arrangement holds the two shaft seals 36o and 38o at an overpressure in the chamber 34o basically spaced apart while the collar 60o and 62o can move apart axially due to their elasticity. A deformation is therefore only in a certain range of shaft seals 36o and 38o allowed. In the illustrated embodiment, the collar 60o and 62o in the axial direction on the flat ribs 100o and 102 o deferred, leaving the collar 60o and 62o or their sealing lips 64o and 66o radially on the flat ribs 100o and 102 o be pressed. When pressure is released, the two collars 60o and 62o by the spring element 98o again axially from the flat ribs 100o and 102 o pulled down.

The 18 to 20 now schematically illustrate further embodiments in which the formation of the annular chamber 34 indirectly sealed shaft seals are used.

In the in 18 shown embodiment is between the axle body 14p and the hub 12p a ball bearing 104p arranged. The ball bearing 104p includes a cylindrical, radially outer race 106p , which is flat on the inner surface 80p the hub 12p abuts and relative to the hub 12p is fixed. The ball bearing 104p further comprises a cylindrical, radially inner race 108p , which flat on the axle body 14p abuts and relative to the axle body 14p is fixed. Between the two races 106p and 108p are tapered rollers 110p arranged, which is a controlled rotation of the radially outer race 106p around the radially inner race 108p enable. Axially outside are between the two races 106p and 108p two shaft seals 112p and 114p arranged, whose operation similar to the above-described shaft seals 36 and 38 is, with the difference that the shaft seals 112p and 114p radially outside, instead of the hub 12p to contact, with the radially outer race 106p in contact and radially inside, instead of the axle body 14p to contact, with the radially inner race 108p stay in contact. The two shaft seals 112p and 114p cause a seal between the axle body 14p and the hub 12p therefore only indirectly.

Basically, to form an annular chamber 34 Any combination of indirectly and directly sealing shaft seals conceivable. In the in 18 shown embodiment, the annular chamber 34p for example, by the axially inner, directly sealing Welldichtring 36p and the axially outer, indirectly sealing shaft seal 108p established. More precisely, the annular chamber 34p So through the lateral surface 58p of the axle body 14p , the inner surface 80p the hub 12p , the axially inner shaft seal 36p , the axially outer shaft seal 112p as well as through the annular chamber 34p facing surfaces of the two races 106p and 108p of the ball bearing 104p limited.

19 shows a further embodiment, which differs from the previous example in that the axle assembly shown here, a second between the axle body 14q and the hub 12q arranged ball bearing 116q with corresponding shaft seals 118q and 120q includes. In the example shown is the ball bearing 116q axially further out than the ball bearing 104q appropriate. In an embodiment with two ball bearings 104q and 116q it is of course conceivable, the annular chamber 34q also elsewhere than in 19 arranged to arrange. By appropriate placement of the immediately sealing shaft seal 36q it is easily possible, the annular chamber 34q by interaction of the shaft seal 36q each with one of the shaft seals 112q . 114q . 118q and 120q to build.

20 shows a further embodiment, which differs from the example 19 this distinguishes that the annular chamber 34r here between the two indirectly sealing shaft seals 114r and 118r the adjacent, spaced ball bearings 104r and 116r is formed. On an immediately sealing shaft seal is completely omitted here.

The ones described below 21 to 26 now show embodiments of a Fahrzeugachsbrouppe, which does not require the axially inner and axially outer shaft seal, in contrast to the embodiments described above.

As in 21a and 21b is shown in such an axle assembly, the annular chamber 34s by one with the inner surface 80s the hub 12s connected ring profile 122s with U-shaped cross section, its side walls 124s and 126s axially, and one between the side walls 124s and 126s arranged sealing ring 128s limited. The sealing ring 128s is in this case with respect to the axle body 14s rotation. The first pressure medium line 28s is also with respect to the axle body 14s firmly and extends through the sealing ring 128s to enter the annular chamber 34s to flow into. The second pressure medium line 40s extends from the annular chamber 34s first through the ring profile 122s and then through the hub 12s , The sealing ring 128s can be given for example by a commercially available double-acting Simmerring ^® .

The sealing ring 128s is both radially inward and radially outward with a main seal lip 130s respectively. 132s each provided by one of a hose spring 134s respectively. 136s generated contact force against the side wall 124s respectively. 126s is pressed and thus a seal between the two side walls 124s respectively. 126s causes. With a rotation of the hub 12s around the axle body 14s is the sealing ring 128s relative to the axle body 14s stuck while with the side walls 124s respectively. 126s in contact with the main sealing lips 130s respectively. 132s over the inner surfaces of the side walls 124s respectively. 126s slide. The sealing ring 128s is also adjacent to the annular chamber 34s both radially inward and radially outward with a collar 138s respectively. 140s Mistake. The collars 138s and 140s each have a sealing lip 142s respectively. 144s on, at least at overpressure in the annular chamber 34s like this in 21b is shown, with the inner surfaces of the side walls 124s respectively. 126s in contact and in addition to the main sealing lips 130s and 132s create a sealing effect. Im in 21a embodiment shown are the sealing lips 142s and 144s at normal pressure not in contact with the side walls 124s respectively. 126s and are only at an overpressure in the chamber 34s against the inner surfaces of the side walls 124s respectively. 126s pressed. It goes without saying that the collar 138s and 140s with the sealing lips 142s and 144s even at a normal pressure (ambient pressure) in the chamber 34s in contact with the side walls 124s respectively. 126s can stand.

At an overpressure in the chamber 34s a pressing out of the sealing ring 128s from the side walls 124s respectively. 126s of the ring profile 122s To counteract, a holder is provided as a stop 146S on the first pressure medium line 28s near its mouth into the chamber 34s is realized. The sealing ring 128s can be axially against the stop 146S support. In addition, in the area of the open ends of the side walls 124s respectively. 126s of the ring profile 122s on the inner surfaces of the side walls 124s respectively. 126s extending in the circumferential direction retaining ribs 148S respectively. 150s present, which is an axial movement of the sealing ring 128s from the ring profile 122s Prevent as soon as the head sealing lips 130s respectively. 132s against the retaining ribs 148S respectively. 150s bump.

The 22a and 22b further show how an axial pressing out of the sealing ring 128t from the side walls 124t respectively. 126t of the ring profile 122t can also be encountered. The embodiment shown here differs from that in the 21a and 21b shown example in that on the inner surfaces of the side walls 124t respectively. 126t circumferentially extending ribs 152t respectively. 154T are present, where the collar 138t respectively. 140t positive fit, at least at an overpressure in the chamber 34t support axially. As in 22a shown are the collars 138t respectively. 140t at normal pressure still from the ribs 152t respectively. 154T spaced and come only at an overpressure with the ribs 152t respectively. 154T in contact. It is understood that even at normal pressure contact between the collar 138t respectively. 140t and the ribs 152t respectively. 154T already exist.

The 23a and 23b show a variation of the embodiment of the 22a and 22b , The difference here is that on the inner surfaces of the side walls 124U respectively. 126U existing ribs 156U respectively. 158U are designed as flat ribs. In this embodiment rely on a positive pressure in the chamber 34u the collar 138u respectively. 140u not in the axial direction on the flat ribs 156U respectively. 158U but off in the axial direction on the flat ribs 156U respectively. 158U deferred, leaving the collar 138u and 140u or their sealing lips 142U and 144U radially on the flat ribs 156U respectively. 158U be pressed. This embodiment is especially advantageous when pressure regulation is to take place while the vehicle is traveling. So they are at an overpressure in the chamber 34u occurring friction forces between the sealing lips 142U respectively. 144U and the flat ribs 156U respectively. 158U significantly less than between the collar 138t respectively. 140t and the ribs 152t respectively. 154T according to the embodiment of the 22a and 22b ,

Other embodiments are in the 24 to 26 given. These embodiments basically correspond to those of 21 to 23 , One difference, however, is that the side walls 124v . 124W . 124x respectively. 126v . 126W . 126x the ring profiles 122v . 122w . 122x not axial, but radial. The above explanations to the 21 to 23 are therefore analogous to the 24 to 26 apply, with the difference that those elements or features that have been described above with axial alignment are now to be designated with radial orientation, and those elements or features that have been described above with radial alignment are now to be designated with axial alignment.

It is understood that further variations of these embodiments are conceivable. In particular, it is possible to further from the embodiments described above according to the 3 to 17 known features with the embodiments of 21 to 26 to combine. Thus, it is conceivable to make the collar of the sealing ring longer, so that the collar protrude into existing on the inner surfaces of the side walls of the annular profile annular grooves. At an overpressure in the annular chamber, these collars are then pressed against the walls of the annular grooves.

Claims (22)

Vehicle axle assembly ( 10 ), with a hub ( 12 ; 12a - 12r ), which about a central longitudinal axis (A) rotatably on a cylindrical axle body ( 14 ; 14a - 14r ) is mounted, and an axially inner shaft seal ( 36 ; 36a - 36q ; 114r ) and an axially outer shaft seal ( 38 ; 38a - 38o ; 112p ; 112q ; 118r ) for direct or indirect sealing between the axle body ( 14 ; 14a - 14r ) and the hub ( 12 ; 12a - 12r ), characterized by - an annular chamber ( 34 ; 34a - 34r ), between the two shaft seals, the axle body ( 14 ; 14a - 14r ) and the hub ( 12 ; 12a - 12r ) is formed; - a first pressure medium line ( 28 ; 28a - 28r ) extending through the axle body ( 14 ; 14a - 14r ) or one of the two shaft seals and into the annular chamber ( 34 ; 34a - 34r ) opens; and - a second pressure medium line ( 40 ; 40a - 40r ) arising from the annular chamber ( 34 ; 34a - 34r ) through the hub ( 12 ; 12a - 12r ) and for connection to one on the hub ( 12 ; 12a - 12r ) fixed wheel is configured. A vehicle axle assembly according to claim 1, characterized in that at least one of the shaft sealing rings adjacent to the annular chamber ( 34 ; 34a - 34r ) radially inward or radially outward with a collar ( 60a - 60g ; 60l - 60o . 62a - 62d ; 62l - 62o ) is provided. Fahrzeugachsbompuppe according to claim 2, characterized in that the collar ( 60a ; 60b ; 60e ; 60n ; 60o . 62a ; 62b ; 62n ; 62o ) a sealing lip ( 64a ; 64b ; 64e ; 64n ; 64o . 66a ; 66b ; 66n ; 66o ), which at least at an overpressure in the chamber ( 34a ; 34b ; 34e ; 34n ; 34o ) with the axle body ( 14a ; 14b ; 14e ; 14n ; 14o ) respectively the hub ( 12a ; 12b ; 12e ; 12n ; 12o ) is in contact. Fahrzeugachsbompuppe according to claim 2, characterized in that on the lateral surface ( 58c ) of the axle body ( 14c ) with respect to a radially inner collar ( 60c . 62c ) an annular groove ( 72c . 74c ) in which the collar ( 60c . 62c ) projects radially. Fahrzeugachsbompuppe according to claim 2 or 4, characterized in that on an inner surface ( 80f ) the hub ( 12f ) with respect to a radially outer collar ( 60f ) an annular groove ( 72f ) in which the collar ( 60f ) projects radially. Fahrzeugachsbompuppe according to claim 2, characterized in that on the lateral surface ( 58d ; 58l ; 58m ) of the axle body ( 14d ; 14l ; 14m ) a circumferentially extending rib ( 76d ; 76l ; 76m . 78d ; 78l ; 78m ) is present, at which a radially inner collar ( 60d ; 60l ; 60m . 62d ; 62l ; 62m ) at least at an overpressure in the chamber ( 34d ; 34l ; 34m ) is axially supported. Vehicle axle assembly according to claim 2 or 6, characterized in that on an inner surface ( 80g ) the hub ( 12g ) a circumferentially extending rib ( 76g ) is present, at which a radially outer collar ( 60g ) at least at an overpressure in the chamber ( 34g ) is axially supported. Fahrzeugachsbompuppe according to claim 6 or 7, characterized in that the rib ( 76d ; 76g ; 76l ; 76m . 78d ; 78g ; 78l ; 78m ) in one piece with the axle body ( 14d ; 14l ; 14m ) or the hub ( 12g ) is trained. Fahrzeugachsbompuppe according to claim 6 or 7, characterized in that the rib ( 76d ; 76g ; 76l ; 76m . 78d ; 78g ; 78l ; 78m ) is formed by a snap ring or O-ring inserted into a groove. Fahrzeugachsbompuppe according to one of claims 6 to 9, characterized in that the rib has a substantially rectangular cross-section. Fahrzeugachsbompuppe according to any one of claims 6 to 10, characterized in that a radially inner collar ( 60d ; 60l ; 60m . 62d ; 62l ; 62m ) a sealing lip ( 64d ; 64l ; 64m . 66d ; 66l ; 66m ), which at least at an overpressure in the chamber ( 34d ; 34l ; 34m ) with the axle body ( 14d ; 141 ; 14m ) or the rib ( 76d ; 76l ; 76m . 78d ; 78l ; 78m ) is in contact, and / or a radially outer collar ( 60g ) a sealing lip ( 64g ), which at least at an overpressure in the chamber ( 34g ) with the hub ( 12g ) or the rib ( 76g ) is in contact. Fahrzeugachsbompuppe according to any one of the preceding claims, characterized in that between the two shaft sealing rings ( 36h ; 36i . 38h ; 38i ) on the lateral surface ( 58h ; 58i ) of the axle body ( 14h ; 14i ) an annular flange ( 84h ; 84i ) with two elastic, radial side walls ( 86h ; 86i . 88h ; 88i ), wherein the first pressure medium line ( 28h ; 28i ) in the annular flange ( 84h ; 84i ) between the two side walls ( 86h ; 86i . 88h ; 88i ) in the annular chamber ( 34h ; 34i ) opens. Fahrzeugachsbompuppe according to claim 12, characterized in that on an inner surface ( 80i ) the hub ( 12i ) opposite the annular flange ( 84i ) a ring ( 90i ) is fastened with a U-shaped cross section whose side walls ( 92i . 94i ) are directed radially inwardly and the second pressure medium line ( 40i ) through the ring ( 90i ) between its side walls ( 92i . 94i ) in the hub ( 12i ). Fahrzeugachsbompuppe according to any one of the preceding claims, characterized in that the two shaft sealing rings ( 36j ; 36l ; 36o . 38j ; 38l ; 38o ) are axially rigidly coupled together. Fahrzeugachsbompuppe according to any one of the preceding claims, characterized in that the two shaft sealing rings ( 36k ; 36m ; 36n ; 36o . 38k ; 38m ; 38n ; 38o ) are axially elastically coupled together. Fahrzeugachsbompuppe according to any one of the preceding claims, characterized in that at least one of the two shaft sealing rings ( 114r . 112p ; 112q ; 118r ) in between the axle body ( 14p ; 14q ; 14r ) and the hub ( 12p ; 12q ; 12r ) arranged ball bearing ( 104p ; 104q ; 104r . 116r ) is integrated. Fahrzeugachsbompuppe according to any one of the preceding claims, characterized in that a valve for pressure relief of the annular chamber ( 34 ; 34a - 34r ) is available. Vehicle axle assembly ( 10 ), with a hub ( 12s - 12x ), which about a central longitudinal axis (A) rotatably on a cylindrical axle body ( 14s - 14x ), characterized by - one having an inner surface ( 80s - 80x ) the hub ( 12s - 12x ) connected ring profile ( 122s - 122x ) having a U-shaped cross section whose side walls ( 124s - 124x . 126s - 126x ) extend axially or radially; - one between the side walls ( 124s - 124x . 126s - 126x ), with respect to the axle body ( 14s - 14x ) non-rotating sealing ring ( 128s - 128x ), which in the ring profile ( 122s - 122x ) an annular chamber ( 34s - 34x ) limited; - a first pressure medium line ( 28s - 28x ), which extends through the sealing ring ( 128s - 128x ) and into the annular chamber ( 34s - 34x ) opens; and - a second pressure medium line ( 40s - 40x ) arising from the annular chamber ( 34s - 34x ) through the ring profile ( 122s - 122x ) and the hub ( 12s - 12x ) and for connection to one on the hub ( 12s - 12x ) fixed wheel is configured. Fahrzeugachsbompuppe according to claim 18, characterized in that the ring profile ( 122s - 122x ) in one piece with the hub ( 12s - 12x ) is formed, in particular is cast. Fahrzeugachsbompuppe according to claim 18 or 19, characterized in that a holder ( 146S ; 146v . 1485 ; 148v . 150s ; 150v ) is provided, which in a ring profile ( 122s ) with axially extending side walls ( 124s . 126s ) the axial position of the sealing ring ( 128s ) and in a ring profile ( 122v ) with radially extending side walls ( 124v . 126v ) the radial position of the sealing ring ( 128v ) fixed. Fahrzeugachsbroup according to one of claims 18 to 20, characterized in that in a ring profile ( 122s ; 122t ; 122U ) with axially extending side walls ( 124s ; 124t ; 124U . 126s ; 126t ; 126U ) the sealing ring ( 128s ; 128t ; 128u ) adjacent to the annular chamber ( 34s ; 34t ; 34u ) radially inward and radially outward with a collar ( 138s ; 138t ; 138u . 140s ; 140t ; 140u ) and that in the case of a ring profile ( 122v ; 122w ; 122x ) with radially extending side walls ( 124v ; 124W ; 124x . 126v ; 126W ; 126x ) the sealing ring ( 128v ; 128W ; 128x ) adjacent to the annular chamber ( 34v ; 34w ; 34x ) axially inwardly and axially outwardly with a collar ( 138V ; 138W ; 138x . 140v ; 140w ; 140x ) is provided. Fahrzeugachsbompuppe according to claim 21, characterized in that in a ring profile ( 122t ) with axially extending side walls ( 124t . 126t ) on the side walls ( 124t . 126t ) of the ring profile ( 122t ) a support structure ( 152t . 154T ) is present, at which the radially inner and the radially outer collar ( 138t . 140t ) at least one Overpressure in the chamber ( 34t ) is axially supported and that in a ring profile ( 122w ) with radially extending side walls ( 124W . 126W ) on the side walls ( 124W . 126W ) of the ring profile ( 122w ) a support structure ( 152W . 154W ) is present, at which the axially inner and the axially outer collar ( 138W . 140w ) at least at an overpressure in the chamber ( 34w ) is supported radially.

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