vehicle wheel axle assembly

专利摘要:
VEHICLE WHEEL AXLE ASSEMBLY The invention relates to a vehicle wheel axle assembly (10), comprising a hub (12) that is mounted on a cylindrical wheel axle body (14) so that it can rotate around a central longitudinal geometric axis (A), and comprising an inner axial and an outer axial seal ring (36, 38) in order to provide an indirect or direct seal between the wheel axle body (14 ) and the hub (12). In order to allow an autonomous pressure medium supply in a vehicle tire, the vehicle wheel axle assembly (10) is characterized by an annular chamber (34) formed between the two axle seal rings (36, 38 ), the wheel axle body (14) and the hub (12), by a first line of pressure medium (28) that extends through the wheel axle body (14) or through one of the two shaft seal (36, 38) and opens to the annular chamber (34), and through a second line of pressure medium (40) that extends out of the annular chamber (34) through the hub (12) and which is designed to be connected to a wheel that is attached to the hub (...).
公开号:BR112015009215B1
申请号:R112015009215-2
申请日:2013-09-20
公开日:2021-01-05
发明作者:Konstantinos Tsiberidis
申请人:Gv Engineering Gmbh；
IPC主号:

专利说明:

[001] The present invention relates generally to the field of vehicles with tires and, in particular, to a vehicle wheel axle assembly comprising an integrated pressure medium line for feeding a pressure medium into a tire.
[002] In order to fill a vehicle tire with a pressure medium, usually compressed air, it is known to provide a valve on the vehicle wheel, by means of which the pressure medium can be introduced into the tire. In cars, trucks or commercial vehicles, such valves are conventionally arranged in the region of a wheel rim, on which the tire is mounted, in a way that is easily accessible to a person who wants to inflate the tire. Typically, in this case, in relation to the vehicle, a source of external pressure medium is connected to the tire valve, conventionally by means of a hose, in order to be able to check and, if necessary, correct the tire pressure. .
[003] This method of regulating pressure of the tire fundamentally has the drawback that an adjustment can be carried out only in places where there is a source of pressure medium, for example, in gas stations, since an attachment to a source pressure medium external to the vehicle is always necessary. In principle, it would be desirable to be able to adjust the tire pressure independently, for example, in the case of long-distance road transport, in order to adapt the tire pressure quickly to changing load conditions, road surfaces and ambient temperatures.
[004] The purpose of the invention is, therefore, to indicate a solution, by means of which the pressure medium can be fed and removed from a vehicle tire independently and preferably also during displacement.
[005] Starting from a vehicle wheel axle assembly comprising a hub, which is mounted on a cylindrical wheel axle body so that it can rotate around a central longitudinal geometric axis, and an axle seal ring internal axial and an external axial for indirect or direct sealing between the wheel axle body and the hub, this objective is achieved according to the invention by means of an annular chamber that is formed between the two axle sealing rings, the wheel axle body and the hub, by a first line of pressure medium which extends through the wheel axle body or one of the two shaft seal rings and opens into the annular chamber, and by a second line of medium of pressure that extends out of the annular chamber through the hub and is designed to be connected to a wheel that is attached to the hub.
[006] An arrangement like this has the advantage of allowing a pressure medium to be fed from a fixed part of the vehicle, namely the wheel axle body, in the hub, which rotates in relation to the wheel axle body and, consequently, on the wheel that rotates around the wheel axle body, without having to provide additional seals for this purpose. This is achieved by providing an annular chamber between the two shaft sealing rings that establishes a connection between the body of the fixed wheel axle and the rotating wheel which is suitable for transferring a pressure medium.
[007] In order to form the annular chamber, according to the invention, a substantially hollow cylindrical space is used, which is located between the body of the wheel axle and the hub. The sealing rings of the inner and outer axial axes are arranged axially spaced from one another in such a way that the annular chamber is formed.
[008] The seal between the wheel axle body and the hub by means of the axle seal rings can in this case be obtained directly or indirectly. In the case of direct sealing, the axle seal ring is directly in contact with both the wheel axle body and the hub, thereby obtaining a seal between the wheel axle body and the hub only through the ring shaft seal. In the case of indirect sealing, additional elements are arranged between the axle seal ring and the wheel axle body and / or the hub so that the axle seal ring is not directly in contact with the wheel axle body. and / or the cube.
[009] Next, reference is made first to shaft seal rings that seal directly. The case of shaft sealing rings that indirectly seal will be described below. In the case of shaft sealing rings that seal directly, the annular chamber is bounded by the side surface of the cylindrical wheel axle body, the inner surface of the hub facing the side surface of the wheel axle body, and the two shaft seal.
[0010] The first line of pressure medium is provided to transfer a pressure medium, such as, for example, compressed air, from a source of pressure medium located internally in the vehicle to the annular chamber. The source of the pressure medium can be, for example, a compressor or a pressure medium container, in which, for example, compressed air is stored. The first line of pressure medium is fixed in relation to the wheel axle body. It can pass outside the wheel axle body and be fastened to it by means of suitable clamps. If the first line of pressure medium passes outside the wheel axle body, it can preferably extend axially through one of the two shaft seal rings before opening into the annular chamber. It is also possible to pass the first line of pressure medium at least in sections through the body of the wheel axle, for example, through a hole formed in the body of the wheel axle. The first line of pressure medium can then open directly in the annular chamber, that is, without passing through one of the shaft sealing rings.
[0011] The second line of pressure medium is used to transfer the pressure medium out of the annular chamber and, at its remote end of the chamber, is designed to be connected to a wheel that is attached to the hub. The second line of pressure medium extends out of the annular chamber and can, in this case, pass at least in sections through the hub, for example, through a hole in the hub. A wheel attached to the hub may comprise a wheel rim and a tire, which is mounted on the wheel rim and has a valve for attaching the second line of pressure medium. The second line of pressure medium can therefore pass to the tire valve and be attached to it so that a supply of pressure medium to the tire can be performed. The tire valve can advantageously be configured as a Y connection to allow a supply of pressure medium selectively through the second line of pressure medium or through another supply line, for example, through a coupling mentioned above in a power source. external pressure medium.
[0012] The two axle sealing rings can be fixed to the hub, for example, by friction fitting, and, by rotating the hub around the body of the wheel axle, they can slide along the side surface of the wheel axle body. Also, both axle sealing rings can be attached to the wheel axle body and, by rotating the hub around the wheel axle body, they can slide along the inner surface of the hub. If the first line of pressure medium opens to the annular chamber through one of the two shaft sealing rings, then the shaft sealing ring in question must be fixed in relation to the wheel axle body. If the first line of pressure medium opens to the annular chamber through the wheel axle body, then the two axle sealing rings can each be individually fixed in relation to the wheel axle body or in relation to the hub.
[0013] The axle assembly described is particularly advantageous in that, in conventional axle assemblies, for example, trucks, there are typically two mutually adjacent axle sealing rings already provided to ensure the sealing of a wheel bearing between the body of the wheel axle and the hub. The shaft sealing rings are used to prevent lubricant from escaping from the wheel bearing on the one hand, and particles of dirt or dust from entering the wheel bearing on the other hand. In the solution according to the invention, these components already provided are simply rearranged, that is, spaced axially from each other, in order to form a coupling space between the two shaft sealing rings for the two lines of pressure medium in the shape of the annular chamber. Such a solution is also advantageous because, for example, in the case of a truck or commercial vehicle, the vehicle typically already has a source of pressure medium in the form of an air compressor for the brake system, which can be used for tire pressure regulation.
[0014] When the pressure medium is fed through the first line of pressure medium, an overpressure, that is, a pressure greater than atmospheric pressure, appears in the annular chamber and tries to press the two shaft sealing rings axially one outward from the other. In order to counterbalance the axial separation of the two shaft seal rings, at least one of the two shaft seal rings, preferably, however, both can be provided with a radial collar adjacent to the annular chamber.
[0015] If a shaft seal ring is attached to the hub, then a collar like this can be formed on the radially internal shaft seal ring. If an axle seal ring is attached to the wheel axle body, then the collar can be formed on the radially external axle seal ring. In this case, the collar can be configured in such a way that, at normal pressure, that is, at approximately atmospheric pressure, it is in contact with the lateral surface of the wheel axle body. It is also conceivable that the collar at normal pressure is still spaced from the lateral surface of the wheel axle body and, only by means of an overpressure in the chamber, deform elastically in such a way that it comes into contact with the lateral surface of the axle body. wheel. In both cases, the frictional force generated by the collar on the contact surface leads to better axial fixation of the respective shaft seal ring. In addition, in the collar, an annular spring element can be additionally provided, whose spring action further intensifies the frictional force generated on the contacting surface.
[0016] The collar may furthermore have a sealing lip, which, at least in the case of an overpressure in the chamber, is in contact with the wheel axle body and / or the hub. The sealing lip can be provided predominantly for the purpose of producing, in addition to the collar fixing effect, an even more improved sealing of the annular chamber.
[0017] In order to combat even more effectively a possible separation of the two shaft seal rings, an annular groove may be provided on the side surface of the wheel shaft body opposite to a radially internal collar of an axle seal ring, into which the collar protrudes radially. Similarly, an annular groove can be provided on the inner surface of the hub opposite to a radially external ring of the shaft sealing ring, into which the collar protrudes radially. In the event of an overpressure in the chamber, the collar is then pressed towards the groove wall, and supported in it, so that the shaft sealing ring maintains its axial position.
[0018] An axial separation of the two shaft sealing rings can also be combated by providing a rib on the side surface of the wheel shaft body that extends in the peripheral direction and in which a radially internal collar of a shaft sealing ring it is axially supported at least in the case of an overpressure in the chamber. Similarly, a rib may be provided on the inner surface of the hub, which extends in the peripheral direction and in which a radially external collar of a shaft seal ring is axially supported at least in the case of overpressure in the chamber.
[0019] A rib like this can, in this case, be built integrally with the wheel axle body and / or the hub, but it can alternatively be formed by a retaining ring or O-ring of elastomeric material that is inserted in a slot. According to one embodiment, the rib has a substantially rectangular cross section.
[0020] A radially internal collar can, in turn, have a sealing lip, which, at least in the case of an overpressure in the chamber, is in contact with the wheel axle body or the rib. Similarly, a radially external collar may have a sealing lip, which, at least in the case of an overpressure in the chamber, is in contact with the hub or rib. A sealing edge like this can, in addition to the support function achieved by the interaction of the collar and the rib, provide an improved sealing of the annular chamber.
[0021] According to another configuration, between the two shaft seal rings on the lateral surface of the wheel axle body, an annular flange comprising two flexible radial side walls is mounted. The first line of pressure medium can then open into the annular chamber on the annular flange between the two side walls. Given an arrangement like this, the chamber sealing can be carried out in which the side walls of the annular flange in the event of an overpressure in the chamber are elastically deformed, that is, pressed to separate from each other and consequently pressed axially against one of the respective rings shaft seal.
[0022] In a development of the previously described configuration, on the inner surface of the cube opposite the annular flange, a ring with a U-shaped cross section is attached, whose side walls are directed radially inward and fit the flexible side walls of the flange cancel. The second line of pressure medium can then extend through the ring between its side walls into the interior of the hub. The sealing of the annular chamber can in this case be carried out in which, in the event of an overpressure in the chamber, the side walls of the annular flange deform elastically and, in this case, are pressed axially against a respective side wall of the U-shaped ring.
[0023] The aforementioned modality, comprising an annular flange with two flexible side walls on the lateral surface of the wheel axle body, as well as a ring with a U-shaped cross section attached to the inner surface of the hub, or the other way around (ring U-shaped body on the wheel axle body and annular flange on the hub), can also be used without the two axle sealing rings, since the annular chamber in this case is already defined by the interaction of the annular flange with the ring with the U-shaped cross section.
[0024] An axial separation of the two shaft sealing rings can also be prevented in that the two shaft sealing rings are rigidly coupled axially to each other. Such a rigid coupling can be achieved, for example, by mounting one or more rigid connection elements between the two shaft sealing rings. The two shaft sealing rings can also be manufactured, for example, cast, as a unit, in which, at the same time, a gap between both shaft sealing rings that is required to supply and / or remove filling air from the shaft. pneumatic, together with the necessary radial through holes, can be easily provided structurally.
[0025] In a similar manner, a separation of the two shaft seal rings can be combated by coupling the two shaft seal rings in an axially flexible manner to each other. A flexible coupling can be carried out, for example, by mounting one or more spring elements between the two shaft sealing rings. The spring element or spring elements in this case can be configured in such a way that they exert a pulling force that combats separation of the shaft sealing rings only when an overpressure prevails in the annular chamber. A combination of rigid and flexible coupling of the two shaft sealing rings is also possible, for example, in order to allow a defined deformation of a specific region of the shaft sealing rings in the axial direction.
[0026] According to an additional modality, at least one of the two shaft sealing rings can be integrated in a ball bearing, which is arranged between the wheel axle body and the hub. In this case, the seal between the wheel axle body and the hub is achieved, not directly through the axle seal ring, but only indirectly. A shaft seal ring like this is preferably arranged between the radially inner race and the radially outer race of the ball bearing in such a way that it forms an external sealing layer for the ball bearing in the region between the raceways that prevents dirt or dust particles penetrate the ball bearing and lubricants escape the ball bearing. The radially inner race of the ball bearing in this case is flat against the lateral surface of the wheel axle body and is fixed in relation to the wheel axle body. The radially outer race of the ball bearing is flat against the inner surface of the hub and is fixed in relation to the hub. In this arrangement, the annular chamber on its side facing the ball bearing is thus delimited by the sealing ring of the integrated shaft and the side faces of the two tracks facing the annular chamber.
[0027] An axial displacement of an axle seal ring like this in the event of an overpressure in the chamber is normally prevented by fixing the ball bearing in relation to the wheel axle body and the hub. Furthermore, it is, however, perfectly feasible in a manner analogous to the previously described shaft seal rings to also provide a support structure for such integrated shaft seal rings, for example, in the form of a groove or rib in one of the lanes, against which a respective collar can be supported at least in case of overpressure in the annular chamber.
[0028] Basically, to form the annular chamber, any desired combination of sealing rings of the shaft that seals indirectly and that seals directly is conceivable. Thus, according to one embodiment, the annular chamber can be defined between an axially internal direct sealing ring of the shaft and an external axial indirect sealing ring of the shaft. An opposite arrangement is also feasible, that is, a delimitation of the chamber by means of an axially internal indirect sealing ring of the shaft and an external axial direct sealing ring of the shaft. If, in a vehicle wheel axle assembly, there are two ball bearings mutually spaced with integrated shaft seal rings, then, according to an additional modality, it is possible to form the annular chamber between the two ball bearings, this that is, between two shaft sealing rings that indirectly seal.
[0029] Finally, a pressure relief valve for the annular chamber can also be provided. Once a supply of the pressure medium has been carried out, an overpressure in the annular chamber can be reduced thereby to prevent both the two lines of pressure medium and the annular chamber from being permanently under high pressure.
[0030] Additional advantageous modalities of the vehicle wheel axle assembly described result from special configurations of the axle seals which are described below.
[0031] According to one embodiment, at least one of the shaft sealing rings, particularly in the collar region, may have a core made of a material that stiffens the shaft sealing ring. The core is made more stable than the material of the residual shaft seal ring and can be designed, for example, by means of a metal reinforcement ring which is embedded in the material of the shaft seal ring. In the event of an overpressure in the chamber, the shaft sealing ring and / or the collar is stabilized by means of the core and is therefore better able to withstand pressure in the chamber.
[0032] In addition, when the nucleus is not only arranged on the collar, it may be that a portion of the nucleus that is arranged in the region of the collar is pivotable in relation to the rest of the nucleus and / or is arranged in an articulated manner in relation to the rest of the core. This can be achieved in that the core has a weakening of material, for example, due to thinner material or cutouts in the region of the transition from the portion in the region of the collar to the rest of the core. It is also conceivable that the core is of a multipart construction so that the portion of the core arranged in the region of the collar is separated from the rest of the core. Due to an arrangement like this, it is guaranteed that, in the event of an overpressure in the chamber, despite the reinforcement provided by the core, the collar can deform sufficiently to be sealed in contact with the lateral surface of the wheel axle body and / or the inner surface of the cube.
[0033] In all embodiments of the vehicle wheel axle assembly according to the invention, at least one axle seal ring is used, which seals the space between the wheel axle body and the hub. Such shaft sealing rings conventionally have an empty space between their radially external sealing surface and their radially internal sealing surface. According to an advantageous embodiment of the invention, said void space can be filled with lubricant, which can gradually pass through suitable exits from the shaft sealing ring to the dynamically loaded sealing surface, that is, on the sealing surface on which , due to the rotation of the hub around the body of the wheel axle, a relative movement appears between the seal ring of the axle and the surface of the opposite component. In this way, permanent lubrication occurs at this point, which significantly reduces the friction load of the seal and consequently increases its service life markedly. In known shaft sealing rings, said void space is opened in the axial direction. Depending on the installation situation, the shaft seal ring therefore has to be modified to make this axial opening of the void closed in order to prevent the filling lubricant from escaping through this opening.
[0034] In advantageous embodiments of the shaft assembly according to the invention, at least one of the shaft seal rings has at least one channel, which extends from an internal void space of the shaft seal in a substantially radial direction to a peripheral surface of the shaft seal ring that is in a region between the collar and a main seal lip of the shaft seal ring. Through a channel like this, lubricant located in the empty space can pass to the collar and the main sealing lip and, there, provide lubrication and permanent cooling of the sealing surfaces of the shaft sealing ring in the wheel axle body and / or the cube.
[0035] For the purpose of a permanent supply of lubricant, the empty space on the sealing ring side of the remote shaft of the annular chamber can be provided with a cover. An annular cover can be attached, for example, between the substantially axial members of the shaft sealing ring which enclose the void and consequently can seal the void in an outward direction. In this case, the empty space can extend continuously in the peripheral direction of the shaft seal ring or only along part of the peripheral direction of the shaft seal ring. In embodiments, in which the first line of pressure medium extends through the shaft sealing ring, the first pressure line can also pass through the cover.
[0036] The sealed void can be filled with a lubricant and serve as a lubricant tank, which gradually releases lubricant to lubricate and cool the sealing surfaces of the shaft sealing ring through at least one channel. Axle sealing rings with a pre-loaded lubricant tank can be prefabricated and adapted as “cwVqnwdrifíecpVgu” shaft sealing rings in a vehicle wheel axle assembly according to the invention.
[0037] According to a development, in the empty space there may be a foam material like sponge, which fills at least part of the empty space and overlaps at least one channel. Here, “sponge type” is understood to mean a specific absorptive capacity and / or the general ability to absorb liquid and so it is evident that, instead of foam material, other materials with comparable properties can be employed. The arrangement of a sponge-like foam material directly in front of and / or above a channel has the effect that lubricant located in the empty space of the shaft seal ring cannot immediately flow out through the channel, but is initially absorbed and stored foam material before it is gradually released into the channel. An intermediate space between the collar and the main sealing lip can also be filled at least partially with a sponge-like foam material. Lubricant that passes out of the sealing ring gap through at least one channel into this intermediate space can then be absorbed by the foam material and then distributed evenly on the sealing surfaces on the lateral surface of the wheel axle body and / or on the inner surface of the cube. Preferably, the foam material fills the entire void formed between the collar, the main sealing lip and the wheel axle body and / or the hub and is in particular contact with the collar, the main sealing lip and the wheel axle body and / or hub to provide proper lubrication and cooling of the sealing surfaces of the axle seal ring.
[0038] In addition, an internal void space of the external axial shaft seal ring and an internal void space of the internal axial shaft seal ring can be connected to each other by at least one line. A line like this allows lubricant to pass from one empty space to another, as a result of which lubricant located in an empty space can be distributed in both hollow spaces. In the case of shaft seal rings that are rigidly coupled to each other, the line can be run through connecting elements arranged between the shaft seal rings. If the two shaft seal rings are manufactured as a unit, the line can be passed through portions that connect the two shaft seal rings together.
[0039] The line can extend in the axial direction. In order to achieve a better transport of lubricant in particular from an empty space to the empty space of the other shaft seal ring - which may be necessary if only one of the two hollow spaces store lubricant and this lubricant must also be used to lubricate the other shaft seal ring -, the line may also ascend radially and / or extend obliquely against the main rotation direction of the hub of one shaft seal ring in the direction of the other shaft seal ring. Thus, in the case of shaft sealing rings with a radially internal collar, that is, shaft sealing rings, which, by rotating the hub around the wheel axle body, corroborate the centrifugal forces with the hub. act on the shaft sealing rings are used. Since the lubricant is rotated radially outward from the shaft sealing rings by virtue of the centrifugal force, it can flow relatively easily through a radially rising line. Similarly, the lubricant, because of its inertia, is moved more slowly than the shaft sealing rings, so that it can also flow relatively easily through a line that extends against the main rotation direction of the rings shaft seal. In the case of shaft seal rings with an external axial collar that are locked so as not to rotate in relation to the wheel axle body, such centrifugal forces do not arise. However, here too a stroke of the line that ascends radially from one shaft seal ring towards the other shaft seal ring can guarantee a better lubricant transport, because here the lubricant, due to gravity, has a tendency to be collected in the part of the empty space of a shaft seal ring that is close to the base. The lubricant can then flow easily through a radially ascending line (which, in the region of the shaft seal rings which is close to the base, has a downward stroke from one shaft seal ring to the other shaft seal ring) of the empty space of one shaft seal ring to the empty space of the other shaft seal ring.
[0040] If there is a sponge-like foam material in the hollow spaces of the two shaft sealing rings, the foam material fills the hollow spaces preferably in such a way that the openings of the line are not covered by the foam material, so which lubricant can flow unimpeded through the line. In a concrete embodiment, the foam material may have, for example, a closing surface that extends in the axial direction and is on the far side of an inlet and / or outlet of the line. On the closing surface, moreover, an axially extending partition provided with through openings can be provided in the shaft seal ring and subdivide empty space in a part, which is filled with foam material, and a part, which is free foam material and serves as a lubricant tank. The foam material communicates with the lubricant tank through the through openings.
[0041] According to an additional aspect, the objective mentioned in the introduction is achieved by means of a vehicle wheel axle assembly comprising a hub, which is mounted on a cylindrical wheel axle body so that it can rotate in around a central longitudinal geometric axis. An annular profile with a U-shaped cross section is located on an internal surface of the cube, the side walls of which extend axially or radially. Sealed between the side walls is a sealing ring, which is locked so as not to rotate in relation to the wheel axle body and the annular profile delimits an annular chamber. A first line of pressure medium extends through the sealing ring and opens into the annular chamber. A second line of pressure medium, extending out of the annular chamber through the annular profile and the hub, is designed to be connected to a wheel that is attached to the hub.
[0042] This modality of the vehicle wheel axle assembly allows the formation of an annular chamber without the two axle sealing rings. Instead, the annular chamber is bounded only by the annular profile, which is connected to the inner surface of the hub, and the sealing ring, which is disposed between the side walls of the annular profile.
[0043] The annular profile connected to the internal surface of the cube can be configured as a separate part, which is attached to the internal surface of the cube, but it can also be formed integrally with the cube, for example, fused together with the cube body, if the cube is a molten part.
[0044] As in the case of the vehicle wheel axle assembly first described, a pressure medium supply causes the annular chamber to overpressure, which here attempts to press the sealing ring axially out of the annular profile.
[0045] In order to counterbalance a pressure like this of the sealing ring, a clamp can be provided, which, in the case of side walls extending axially from the annular profile, fixes the axial position of the sealing ring and, in the case of side walls extending radially from the annular profile, fix the radial position of the sealing ring. Such a clamp can be made, for example, in the form of a stop in the first line of pressure medium close to where this line opens in the annular chamber, against which the sealing ring stop is axially supported in the case of side walls which extend axially from the annular profile and radially in the case of side walls extending radially from the annular profile. A support can also be provided in the annular profile, for example, in the form of a peripheral rib that is formed within a side wall or both side walls of the annular profile. In addition, the sealing ring adjacent to the annular chamber can be provided, in the case of side walls extending axially from the annular profile, radially in and radially outside and / or, in the case of side walls extending radially from the annular profile, axially inside and axially outside with a collar, which, at least in the case of overpressure in the chamber, is pressed against the side walls of the annular profile and, due to the frictional force that arises, it contributes, in the case of side walls that extend axially, for axial fixation of the seal ring and / or, in the case of radially extending side walls, for radial fixation of the seal ring. In the case of side walls extending axially from the annular profile, the collars radially internal and radially external can also be positively supported axially in the annular chamber and, in the case of side walls extending radially from the annular profile, the collars axially internal and axial external can be positively supported radially in the annular chamber, for example, in a support structure that is arranged inside the lateral walls of the annular profile. A support structure like this can be configured analogously to the vehicle wheel axle assembly first described, for example, in the form of a groove or rib, on which the respective collar can be supported at least in the event of an overpressure in the annular chamber .
[0046] As in the case of the vehicle wheel axle assembly described above, additional advantageous modalities arise as a result of special sealing ring configurations. Thus, here also the sealing ring provided, particularly in the region of at least one of the two collars, can have a core made of a material that stiffens the sealing ring, and a portion of the core arranged in the region of a collar can be pivotable and / or arranged in an articulated manner with respect to the rest of the core. In addition, the sealing ring can have at least one channel, which extends outside an internal void space in the sealing ring, in the case of an annular profile with axially extending side walls, in the substantially radial and / or direction , in the case of an annular profile with radially extending side walls, in a substantially axial direction to a peripheral portion of the seal ring which lies in a region between a collar and a major seal ring of the seal ring. In addition, the void space on the remote sealing ring side of the annular chamber can be provided with a lid and the void space so sealed can be filled with a lubricant that can be gradually released to lubricate the sealing surfaces of the sealing ring. In addition, a sponge-like foam material can be arranged in the empty space, which fills at least part of the empty space and overlaps at least one channel. An intermediate space between the collar and the main sealing lip can similarly be filled at least partially with a sponge-like foam material.
[0047] With all the previously described modalities, an autonomous tire pressure regulation can be represented. Here, “tire pressure regulation” means, on the one hand, a tire pressure regulation that ensures compliance with a desired tire pressure upon request or automatically, and, on the other hand, a desired change of pressure. tire pressure in order to adapt the tire pressure, for example, to changed conditions (load, temperature etc.), or also a combination of both. In order to carry out an automatic tire pressure regulation, it is possible to make use of signals from sensors or detectors that, in any case, already exist in many vehicles with the purpose, for example, of varying the division of the braking force between a front wheel axle and a vehicle rear axle depending on the load. What can be evaluated for this purpose are, for example, signs of an apparatus that indicate the extent of elastic deflection depending on the load on a vehicle's rear wheel axle, or signs that indicate the pressure in pneumatic spring elements of a vehicle. wheel axle, or a signal from a trailer coupling electrical connector that communicates that a trailer is attached to the vehicle, etc.
[0048] Below is now a detailed description of the various modalities of a vehicle wheel axle assembly according to the invention with reference to the accompanying schematic drawings. These show: figure 1: a longitudinal sectional view of a vehicle wheel axle assembly according to the invention in a general view; figure 2: part of the longitudinal sectional view of the vehicle wheel axle assembly of figure 1 on an enlarged scale and with a modification to supply a tire sealing means; figures 3a and 3b: a detailed view of an embodiment comprising two shaft sealing rings, which both have a radially internal collar; figures 4a and 4b: a detailed view of an embodiment comprising two shaft sealing rings, which both have a radially internal collar with a spring element; figures 5a and 5b: a detailed view of an embodiment comprising two shaft sealing rings with a radially internal collar and with annular grooves formed in the body of the wheel axle; figures 6a and 6b: a detailed view of an embodiment comprising two shaft sealing rings with a radially internal collar and with ribs formed in the body of the wheel axle; figures 7a and 7b: a detailed view of an embodiment comprising a shaft seal ring with a radially inner collar and a shaft seal ring with a radially outer collar; figures 8a and 8b: a detailed view of an embodiment comprising an axle seal ring with a radially internal collar, an axle seal ring with a radially external collar, and associated annular grooves formed in the wheel and hub axle body; figures 9a and 9b: a detailed view of an embodiment comprising an axle seal ring with a radially inner collar, an axle seal ring with a radially outer collar, and associated ribs formed in the wheel and hub axle body; figures 10a and 10b: a detailed view of an embodiment comprising an annular flange disposed between two shaft sealing rings in the wheel axle body; figures 11a and 11b: a detailed view of an embodiment comprising an annular flange disposed between two shaft sealing rings on the wheel axle body and comprising a U-shaped ring disposed on the hub; figures 12a and 12b: a detailed view of an embodiment comprising two rigidly coupled shaft sealing rings, each of which has a radially internal collar; figures 13a and 13b: a detailed view of an embodiment comprising two flexibly coupled shaft sealing rings, each of which has a radially internal collar; figures 14a and 14b: a detailed view of an embodiment comprising two shaft sealing rings rigidly coupled with a radially internal collar and comprising associated ribs formed in the body of the wheel axle; figures 15a and 15b: a detailed view of an embodiment comprising two shaft sealing rings flexibly coupled with a radially internal collar and comprising associated ribs formed in the body of the wheel axle; figures 16a and 16b: a detailed view of an embodiment comprising two shaft sealing rings flexibly coupled with a radially internal collar and comprising flat ribs formed in the body of the wheel axle; figures 17a and 17b: a detailed view of an embodiment comprising two rigidly coupled and flexibly coupled shaft sealing rings, radially internal collars as well as flat ribs formed in the wheel axle body; figure 18: a longitudinal sectional view of an embodiment of an axis assembly comprising a ball bearing, in which the sealing ring of the external axial axis is integrated into the ball bearing; figure 19: a longitudinal sectional view of an embodiment of an axis assembly comprising two ball bearings, in which the sealing ring of the external axial shaft is integrated into the axially internal bearing of the two ball bearings; figure 20: a longitudinal sectional view of an embodiment of a shaft assembly comprising two ball bearings, in which both shaft seal rings are integrated in each case in one of the two ball bearings; figures 21a and 21b: a detailed view of an embodiment comprising a U-shaped annular profile with axially extending side walls and comprising a sealing ring disposed thereon; figures 22a and 22b: a detailed view of an embodiment comprising a U-shaped annular profile with axially extending side walls, a sealing ring disposed thereon, and ribs formed on the side walls; figures 23a and 23b: a detailed view of an embodiment comprising a U-shaped annular profile with axially extending side walls, a sealing ring disposed thereon, and flat ribs formed on the side walls; figures 24a and 24b: a detailed view of an embodiment comprising a U-shaped annular profile with radially extending side walls and a sealing ring disposed thereon; figures 25a and 25b: a detailed view of an embodiment comprising a U-shaped annular profile with radially extending side walls, a sealing ring disposed thereon, and ribs formed on the side walls; figures 26a and 26b: a detailed view of an embodiment comprising a U-shaped annular profile with radially extending side walls, a sealing ring disposed thereon, and flat ribs formed on the side walls; figures 27a and 27b: a detailed view of an embodiment comprising two additionally stiffened shaft sealing rings, which both have a radially internal collar and whose hollow spaces filled with lubricant are connected to each other by the lines; figures 28a and 28b: a detailed view of an embodiment comprising two additionally stiffened shaft sealing rings, which both have a radially external collar and whose hollow spaces are connected to each other by the lines; figures 29a and 29b: a detailed view of an embodiment comprising two additionally stiffened shaft sealing rings, which are manufactured as a unit, have radially external collars, are provided with sponge-like foam material and whose hollow spaces are connected together by a line; figures 30a and 30b: a detailed view of an embodiment comprising a U-shaped annular profile with axially extending side walls and a stiffened sealing ring, which is disposed therein and has an empty space filled with lubricant; figures 31a and 31b: a detailed view of an embodiment comprising a U-shaped annular profile with axially extending side walls and a stiffened sealing ring, which is arranged therein and has an empty space filled with lubricant and whose sealing edge main radially internal is in contact with the wheel axle body; and figures 32a and 32b: a detailed view of an embodiment comprising a U-shaped annular profile with axially extending side walls and a stiffened sealing ring, which is disposed on them, is provided with a sponge-like foam material and radially internal main sealing lip is in contact with the wheel axle body.
[0049] In the following description of modalities, identical reference characters are used to denote elements that are identical or have an identical effect.
[0050] Figure 1 shows in longitudinal section a vehicle wheel axle assembly 10 comprising a hub 12, which is mounted on a hollow cylindrical wheel axle body 14 so that it can rotate about a longitudinal geometric axis central A. In the illustrated embodiment, assembly of the hub 12 is carried out by means of two ball bearings 16 and 18, which are spaced from each other along the axis A. The hub 12 is fastened by means of screws 19 on an axis of drive 20, which extends through the wheel axle body 14 and transmits the drive power generated by an engine not shown to hub 12 in order to rotate it around the wheel axle body 14. Arranged in hub 12 are studs 22, on which a wheel (not shown here) can be placed through a rim on the hub and secured. Additionally attached to the wheel hub 12 is a brake disc 24, which rotates with the wheel hub 12 around the body of the wheel axle 14 so that, in a manner known to those skilled in the art, it can brake a wheel of the wheel. vehicle mounted on hub 12 by means of a brake 26 which is fixed to the vehicle.
[0051] A first line of pressure medium 28 is connected to a source of pressure medium 30 (shown only schematically here), which is arranged in the vehicle and can be, for example, a compressor to generate compressed air or a container of pressurized tire filling medium. In the illustrated embodiment, the first line of pressure medium 28 extends from the source of pressure medium 30 initially outside the body of the wheel axle 14 and then tilts towards a portion 32, which is formed within the body of the axle wheel 14 and opens into an annular chamber 34 formed between the wheel axle body 14 and the hub 12. The portion 32 extending within the wheel axle body 14 can be designed, as illustrated, by a hole in the wheel axle body 14.
[0052] The annular chamber 34 is bounded radially on the outside by the inner surface of the hub 12, radially on the inside by the lateral surface of the wheel axle body 14 and, on either side, by an inner axial seal ring 36 and a outer axial shaft seal ring 38 and consequently provides an empty space, which is sealed directly by shaft seal rings 36 and 38 and extends around the wheel shaft body 14. Extending out of the annular chamber 34 is a second line of pressure medium 40, which, at its remote end of the chamber, is designed to be connected to a wheel that is attached to hub 12. The second line of pressure medium 40 extends in sections through hub 12 , for example, through a hole in hub 12, and additionally along it can be passed, for example, through a rim (not shown in detail here) to a tire valve mounted on the rim. For example, the tire valve can be configured as a Y connection in order to be able to selectively supply a pressure medium via the second pressure medium line 40 or through another supply line, for example, from a medium source. of external pressure, in the tire.
[0053] In order to better understand the following description, particular attention is paid to the fact that, of the components previously described, only the body of the wheel axle 14 as well as the first line of pressure medium 28 and the source of pressure medium 30 are fixed. The components that are connected directly or indirectly to hub 12, however, rotate with hub 12 around the body of the wheel axle 14 as soon as the hub 12 is driven by the drive shaft 20. And so in particular the second middle line of pressure 40 en route and in the course of rotation it is coupled by the annular chamber 34 and / or the sealed void space thereby formed always in a way with fluid transfer to the first line of pressure medium 28. As this coupling is independent of respective rotated position of the hub 12, a supply and / or removal of pressure medium can occur not only in the stationary state, but also during displacement while the hub 12 is rotating. With the arrangement described, therefore, a tire pressure setting can be easily automated.
[0054] According to a development, the described arrangement of the axis assembly 10 can be used not only to supply a gaseous pressure medium, such as, for example, compressed air, but also to supply a liquid pressure medium, for example , a tire sealing means. This can be advantageous particularly in the case of an empty tire. A modality like this requires only slight modifications in the region of the first pressure medium line 28 of the axis assembly 10 shown in figure 1. This is represented by means of the example in figure 2, where the first pressure medium line 28 divides into a fork 42 and the branch then passes into a reservoir 44 containing a tire sealing means. From the reservoir 44 a connection line 45 transfers the pneumatic sealing means if necessary to the pressure medium line 28, in which the connection line 45 opens at a junction 46. In the illustrated embodiment, on the fork 42 a switching mechanism 48 is provided, which in each case releases only one of the two paths of the line, that is, both the main line 28 and the branch that leads to reservoir 44. If the switching mechanism 48 is mounted on the branch, the sealing means of tire located in reservoir 44 is introduced in the first line of pressure medium 28 and transferred from there through the annular chamber 34 to the second line of pressure medium 40 and then to the tire. It is evident that this arrangement for introducing a tire sealing means is merely exemplary. In principle, other arrangements are conceivable, by means of which a tire sealing means can be introduced into the pressure medium line 28, for example, by means of a manual mooring maneuver.
[0055] In an additional embodiment of the shaft assembly 10, a pressure relief device is provided. Since, during a pressure medium supply, an overpressure of up to 10 or even 15 bar is generated in both the first and second pressure medium lines 28 and 40, as well as in the annular chamber 34, it is significant at the end of the pressure regulation perform a pressure relief operation to prevent the pressure medium lines 28 and 40 and the chamber 34 from being constantly under pressure. The pressure relief device can be an exhaust valve, for example, a mechanical valve or an electronically controlled valve, which is arranged at a suitable point in the first line of pressure medium 28, in the second line of pressure medium 40 or in annular chamber region 34 and can provide controlled pressure relief.
[0056] Regarding the detailed configuration of the annular chamber 34 and of the sealing rings of the shaft 36 and 38 that axially delimit it from the side, reference is now made to figures 3 to 17, which illustrate in each case, by means of a detailed view in longitudinal section, different modalities of the annular chamber region 34. In each case, the figure listed with the lower letter “a” shows the state of the arrangement at normal pressure and the figure listed with the lower letter “d” shows the state of the same arrangement in case of overpressure in chamber 34. Elements that are identical or that have an identical effect are furthermore denoted by the same reference characters as in the previous figures, the reference characters for each of the following modalities, meanwhile being supplemented by individual lowercase letters. In each case, unless stated otherwise, for the description of elements that carry identical numerical reference characters, reference is made to the previous descriptions.
[0057] In the embodiment shown in figures 3a and 3b, an inner axial seal ring 36a and an outer axial seal ring 38a are arranged between the wheel axle body 14a and the hub 12a. As shaft sealing rings, commercially available shaft sealing rings, for example, so-called Simmer® rings can be used. Both shaft sealing rings 36a and 38a adhere in each case radially outside by means of friction fit in the hub 12a and are provided in each case radially inside with a main sealing lip 50a and / or 52a, which is pressed by a application force generated by a tubular spring 54a and / or 56a against the wheel axle body 14a and, consequently, makes a direct seal between the wheel axle body 14a and the hub 12a. By rotating the hub 12a around the body of the wheel axle 14a, the two axle sealing rings 36a and 38a as a result of said friction fit, corrotate with the hub 12a, so that the main sealing edges 50a and 52a slide over the side surface 58a of the wheel axle body 14a.
[0058] Both shaft sealing rings 36a and 38a are furthermore provided radially within and adjacent to the annular chamber 34a, in each case, with a collar 60a and / or 62a. Both collars 60a and 62a have a sealing lip 64a and / or 66a, which, at least in the case of an overpressure in chamber 34a, shown in figure 3b, are both in contact with the lateral surface 58a of the axle body 14a and, in addition to the main sealing edges 50a and / or 52a, produce a sealing effect. In the embodiment shown in figure 3a, the sealing edges 64a and 66a at normal pressure do not come into contact with the wheel axle body 14a, but are pressed against the side surface 58a of the wheel axle body 14a only in the case of a overpressure in chamber 34a. It is, however, evident that the collars 60a and 62a with the sealing edges 64a and 66a can already be in contact with the wheel axle body 14a at normal pressure.
[0059] The application force that is generated in the event of an overpressure in the chamber 34a and presses the collars 60a and 62a with the sealing edges 64a and 66a on the side surface 58a of the wheel axle body 14a allows the two shaft seals 36a and 38a stick more strongly to the side surface 58a of the wheel axle body 14a, as a result of which the shaft sealing rings 36a and 38a are able to maintain their axial position for longer. A force, which, in the event of an overpressure in the chamber 34a, can cause the two shaft sealing rings 36a and 38a to separate, is counterbalanced by the pressure of the collars 60a and 62a against the lateral surface 58a of the shaft body. wheel 14a, thereby making it noticeably more difficult for the two axle rings 36a and 38a to separate from each other.
[0060] Figures 4a and 4b show a development of this modality. Here, in a variation of the previous embodiment, collars 60b and 62b are additionally provided with an annular spring element 68b and / or 70b, whose spring action further intensifies the previously described application force that presses collars 60b and 62b with the sealing edges 64b and 66b on the side surface 58b of the wheel axle body 14b. Spring elements 68b and 70b for this purpose can be configured, for example, as tubular springs. Unlike the previous modality, collars 60b and 62b and / or sealing edges 64b and 66b, due to the application force generated by the spring elements 68b and 70b, the normal pressure in chamber 34b, are no longer in contact with the surface side 58b of the wheel axle body 14b. It is also conceivable, however, to provide on the side surface 58b of the wheel axle body 14b opposite collars 60b and 62b and / or sealing edges 64b and 66b a cutout that extends in the peripheral direction, so that the spring action generated by spring elements 68b and 70b is not sufficient enough to press the collars 60b and 62b and / or the sealing edges 64b and 66b under normal pressure in the region of the cutout against the axle body 14b. In this situation, the collars 60b and 62b and / or the sealing edges 64b and 66b would contact the body of the wheel axle 14b in the region of the cutout only in the event of an overpressure in the chamber 34b.
[0061] A device by which an axial separation of the two shaft sealing rings 36 and 38 can be combated even more effectively is shown in the embodiment according to Figures 5a and 5b. This modality differs from the example shown in figures 3a and 3b in that the radially internal collars 60c and 62c of the shaft sealing rings 36c and 38c are projected larger in a radially inward direction, so that they project radially into the annular grooves 72c and / or 74c provided on the side surface 58c of the wheel axle body 14c. In the event of an overpressure in the chamber 34c, the collars 60c and 62c are pressed against the side walls of the annular grooves 72c and 74c, as shown in figure 5b. An axial separation of the two axle rings 36c and 38c is effectively prevented by means of this support. In addition, the contact of the collars 60c and 62c with the walls of the annular grooves 72c and 74c results in an additional sealing of the annular chamber 34c.
[0062] Figures 6a and 6b show an additional example of how an axial separation of the two shaft seal rings 36 and 38 can be combated. The modality shown here differs from the example shown in figures 3a and 3b in that, on the lateral surface 58d of the wheel axle body 14d, there are ribs 76d and 78d, which extend in the peripheral direction and in which the collars 60d and 62d are axially supported at least in the event of an overpressure in chamber 34d. In the modality shown in figure 6a, the necks 60d and 62d at normal pressure are still spaced from the ribs 76d and 78d and come into contact with the ribs 76d and 78d only in the case of an overpressure. It is, however, evident that normal pressure may already have a contact between the collars 60d and / or 62d and the ribs 76d and / or 78d.
[0063] Another modality is shown in figures 7a and 7b. This embodiment differs from the example according to Figures 3a and 3b in that the sealing ring of the inner axle 36e is maintained by means of friction fit in the body of the wheel axle 14e and is therefore locked so as not to rotate in relation to the body of the wheel axle 14e. The shaft sealing ring 36e is provided with a main sealing lip 50e, which is pressed against the hub 12e by means of an application force generated by a tubular spring 54e and, consequently, makes a seal between the body of the shaft. wheel 14e and hub 12e. By rotating the hub 12e around the wheel axle body 14e, the shaft seal ring 36e is stationary in relation to the wheel axle body 14e, while the main sealing lip 50e that is in contact with the hub 12e slides along the inner surface 80e of cube 12e.
[0064] The shaft seal ring 36e is further provided radially on the outside with a collar 60e adjacent to the annular chamber 34e. The collar 60e has a sealing lip 64e, which, at least in the case of overpressure in the annular chamber 34e, shown in figure 7b, is in contact with the inner surface 80e of the hub 12e and, in addition to the sealing lip 50e, produces a sealing effect. In the embodiment shown in figure 7a, the sealing lip 64e at normal pressure is not yet in contact with the hub 12e, but is pressed against the inner surface 80e of the hub 12e only in the event of an overpressure in the chamber 34e. It is, however, evident that collar 60e with sealing lip 64e may already be in contact with hub 12e at normal pressure in chamber 34e.
[0065] This embodiment additionally differs from the example according to Figures 3a and 3b in which here the first line of pressure medium 28e passes not through a hole in the body of the wheel axle 14e which extends parallel to the axis A, but in the void between the hub 12e and the wheel axle body 14e and extends through the inner shaft seal ring 36e before opening in the annular chamber 34e. In this case, a suitable clamp 82e is provided, which secures the first line of pressure medium 28e to the wheel axle body 14e.
[0066] Similarly, the modalities shown in figures 8a and 8b and / or 9a and 9b also differ from the modalities according to Figures 5a and 5b and / or 6a and 6b.
[0067] An additional modality is represented in figures 10a and 10b. This modality differs from the example according to Figures 3a and 3b in that, between the two shaft sealing rings 36h and 38h, an annular flange 84h with two flexible radial side walls 86h and 88h is mounted on the 58h side surface of the body. wheel axis 14h, where the first line of pressure medium 28h opens to the annular chamber 34h on the annular flange 84h between the two side walls 86h and 88h. With this arrangement, the sealing of the chamber 34h is carried out in which, at least in the case of an overpressure in the chamber 34h, the side walls 86h and 88h of the annular flange 84h deform elastically, and thus proceeding are pressed to separate from each other and are axially pressed, in each case, against one of the shaft sealing rings 36h and 38h. This situation is shown in figure 10b.
[0068] A modification of this modality is shown in figures 11a and 11b. In addition to the previous example, here on the inner surface 80i of hub 12i opposite annular flange 84i, a ring 90i with a U-shaped cross section is attached, whose side walls 92i and 94i are directed radially inward and overlap the flexible side walls 86i and 88i of the annular flange 84i. The second line of pressure medium 40i extends between the side walls 92i and 94i through the ring 90i into the hub 12i. In this example, the flexible side walls 86i and 88i of the annular flange 84i in the event of an overpressure in the chamber 34i are pressed, not against the shaft sealing rings 36i and 38i, but against the side walls 92i and 94i of the ring 90i. This situation is shown in figure 11b. A sealing of the annular chamber 34i therefore occurs here between the side walls 86i and 88i of the annular flange 84i and the side walls 92i and 94i of the ring 90i. It is evident that, in this case, the shaft sealing rings 36i and 38i are dispensable, with respect to the sealing of the annular chamber 34i, since the annular chamber 34i is already defined by the interaction of the annular flange 84i with the ring 90i with the U-shaped cross section.
[0069] Figures 12a and 12b show a development of the modality according to Figures 3a and 3b, in which the two shaft sealing rings 36j and 38j are axially rigidly coupled to each other. In the illustrated embodiment, stuck between the two shaft sealing rings 36j and 38j has a connecting element 96j, which extends in the peripheral direction and keeps the two shaft sealing rings 36j and 38j axially spaced rigidly from each other. If the connecting element 96j continuously extends in the peripheral direction, it must have at least one opening to allow a pressure medium to pass through the chamber 34j from the first line of pressure medium 28j to the second line of pressure medium 40j. Advantageously, instead of a continuous connection element with one or more openings, a plurality of mutually spaced individual connection elements can be clamped between the shaft sealing rings 36j and 38j, for example, numerous membranes or individual pins. It is evident that, given such a configuration, axial separation of the two shaft sealing rings 36j and 38j is no longer possible.
[0070] Instead of a rigid coupling, a flexible coupling of the shaft sealing rings can alternatively be provided. This is shown in the embodiment of figures 13a and 13b, which differs from the previous embodiment only in that, instead of the rigid connecting element 96j, a spring element 98k is fastened between the two shaft sealing rings 36k and 38k. The spring element 98k can, for example, be formed, as illustrated, by a helical tension spring, the tensile force of which counterbalances the force arising in the event of an overpressure in the chamber 34k and which would press the two shaft sealing rings 36k and 38k axially out of each other. An axial separation of the two shaft seal rings 36k and 38k is locally restricted or prevented in this way and, by means of pressure relief in the chamber 34k, the two shaft seal rings 36k and 38k take their original position again. It is evident that a plurality of spring elements can alternatively be secured between the two shaft sealing rings 36k and 38k. It is also evident that other types of spring besides a helical tension spring can be used.
[0071] Additional modalities arise as a result of any desired combination of resources of the previously described modalities. Figures 14a and 14b, as well as figures 15a and 15b, show, by way of example, two such combinations. In figures 14a and 14b, the features of the modalities according to Figures 6a and 6b, as well as figures 12a and 12b, are combined. In figures 15a and 15b, the features of the modalities according to Figures 6a and 6b, as well as figures 13a and 13b, are combined.
[0072] Figures 16a and 16b show, as an example, a variation of the modality of figures 15a and 15b. The difference here is based on the fact that the ribs 100n and 102n provided on the side surface 58n of the wheel axle body 14n are configured as flat ribs. In this embodiment, in the event of an overpressure in the 34n chamber, the collars 60n and 62n are not supported in the axial direction on the flat ribs 100n and 102n, but are propelled upwards in the axial direction on the flat ribs 100n and 102n so that the collars 60n and 62n and / or their sealing edges 64n and 66n are pressed radially on the flat ribs 100n and 102n. By means of a pressure relief, the two shaft sealing rings 36n and 38n are pulled by the spring element 98n axially back out of the flat ribs 100n and 102n. This mode is advantageous above all when a pressure regulation is carried out while the vehicle is traveling. The frictional forces that arise in the event of an overpressure in the 34n chamber between the sealing edges 64n and 66n and the flat ribs 100n and 102n are, therefore, noticeably less than between the collars 60m and 62m and the ribs 76m and 78m of according to the modality according to Figures 15a and 15b.
[0073] A possible combination and / or additional variation of the previous modalities is presented by Figures 17a and 17b. Here, the shaft sealing rings 36o and 38o are kept spaced in an axially fixed manner from each other by a rigid connecting element 96o. In addition, a spring element 98o is provided, which is arranged only in the region between the collars 60o and 62o. This arrangement in the event of an overpressure in chamber 34o keeps the two shaft sealing rings 36o and 38o spaced from one another basically in a fixed manner, while the collars 60o and 62o, because of their flexibility, can move axially slightly outward each other's. Deformation is therefore permitted only in a specific region of the shaft sealing rings 36o and 38o. In the illustrated embodiments, collars 60o and 62o are pushed in the axial direction to the flat ribs 100o and 102o, so that the collars 60o and 62o and / or their sealing edges 64o and 66o are pressed radially on the flat ribs 100o and 102o. By means of a pressure relief, the two collars 60o and 62o are pulled by the spring element 98o axially backwards out of the flat ribs 100o and 102o.
[0074] Figures 18 to 20 now schematically represent additional modalities, in which shaft sealing rings that indirectly seal are used to form the annular chamber 34.
[0075] In the embodiment shown in figure 18, a ball bearing 104p is disposed between the wheel axle body 14p and the hub 12p. Ball bearing 104p comprises a radially cylindrical outer race 106p, which lies flat against the inner surface 80p of hub 12p and is fixed in relation to hub 12p. The ball bearing 104p additionally comprises a radially cylindrical inner race 108p, which lies flat against the wheel axle body 14p and is fixed in relation to the wheel axle body 14p. Arranged between the two lanes 106p and 108p are tapered rollers 110p, which allow controlled rotation of the radially outer track 106p around the radially inner track 108p. Axially arranged outside between the two lanes 106p and 108p are shaft seal rings 112p and 114p, a function is similar to the shaft seal rings 36 and 38 above, except that the shaft seal rings 112p and 114p radially on the outside, instead of in contact with hub 12p, they are in contact with the radially outer race 106p and radially on the inside, instead of in contact with the axle body 14p, they are in contact with radially internal track 108p. The two shaft sealing rings 112p and 114p, therefore, only indirectly seal between the body of the wheel axle 14p and the hub 12p.
[0076] In principle, to form an annular chamber 34, any desired combination of shaft seal rings that indirectly and directly seal is conceivable. In the embodiment shown in figure 18, the annular chamber 34p is defined, for example, by the sealing ring of the axially sealing shaft that directly seals 36p and the sealing ring of the external axial shaft that seals 108p indirectly. More precisely, the annular chamber 34p is therefore bounded by the lateral surface 58p of the wheel axle body 14p, the inner surface 80p of the hub 12p, the inner axial shaft seal 36p, the outer axial shaft seal ring 112p and the surfaces - facing the annular chamber 34p - of the two tracks 106p and 108p of the ball bearing 104p.
[0077] Figure 19 shows an additional modality, which differs from the previous example in that the shaft assembly shown here comprises a second ball bearing 116q with corresponding shaft seal rings 118q and 120q, which is disposed between the shaft body wheel 14q and hub 12q. In the illustrated example, the ball bearing 116q is mounted axially in addition to the ball bearing 104q. In a configuration with two ball bearings 104q and 116q, it is certainly conceivable to arrange the annular chamber 34q in a different position than shown in figure 19. Due to the proper positioning of the shaft seal ring that directly seals 36q, it is easily possible to form the annular chamber 34q through the interaction of the shaft seal ring 36q, in each case, with any of the shaft seal rings 112q, 114q, 118q and 120q desired.
[0078] Figure 20 shows an additional modality, which differs from the example according to Figure 19 in which the annular chamber 34r is formed between the two shaft sealing rings that indirectly seal 114r and 118r of the mutually spaced ball bearings adjacent 104r and 116r. Here, a shaft seal ring that seals directly has been completely dispensed with.
[0079] Figures 21 to 26, a description of which is now presented, furthermore show modalities of a vehicle wheel axle assembly which, contrary to the above described modalities, does not require the inner and axial axial sealing ring external.
[0080] As Figures 21a and 21b show, in an axis set like this, the annular chamber 34s is bounded by an annular profile 122s with a U-shaped cross section, which is connected to the inner surface 80s of the cube 12s and whose side walls 124s and 126s extend axially, and by a sealing ring 128s, which is disposed between the side walls 124s and 126s. The sealing ring 128s in this case is locked so as not to rotate in relation to the wheel axle body 14s. The first line of pressure medium 28s is similarly fixed in relation to the wheel axle body 14s and extends through the sealing ring 128s before opening in the annular chamber 34s. The second line of pressure medium 40s extends out of the annular chamber 34s initially through the annular profile 122s and then through the hub 12s. The sealing ring 128s can be made, for example, by a commercially available Simmer® ring on both sides.
[0081] The sealing ring 128s is provided both radially on the inside and radially on the outside with a main sealing lip 130s and / or 132s, each of which is pressed by an application force generated by a tubular spring 134s and / or 136s against the side wall 124s and / or 126s and consequently make a seal between the two side walls 124s and / or 126s. By rotating the hub 12s around the wheel axle body 14s, the sealing ring 128s is fixed in relation to the wheel axle body 14s, while the main sealing edges 130s and / or 132s are in contact with the walls side 124s and / or 126s slide over the inner surfaces of the side walls 124s and / or 126s. The sealing ring 128s is further provided, adjacent to the annular chamber 34s, both radially inside and radially outside with a collar 138s and / or 140s. Collars 138s and 140s each have a sealing lip 142s and / or 144s, which, at least in the case of overpressure in the annular chamber 34s, as shown in figure 21b, are in contact with the inner surfaces of the side walls 124s and / or 126s and moreover with the main sealing edges 130s and 132s produce a sealing effect. In the embodiment illustrated in figure 21a, the sealing edges 142s and 144s at normal pressure do not come into contact with the side walls 124s and 126s and are pressed against the inner surfaces of the side walls 124s and 126s only in the event of an overpressure in the 34s chamber . It is certainly evident that collars 138s and 140s with sealing edges 142s and 144s may alternatively already be in contact with the side walls 124s and 126s at normal pressure (atmospheric pressure) in the 34s chamber.
[0082] In the event of an overpressure in the chamber 34s, in order to counterbalance the pressure of the sealing ring 128s out of the side walls 124s and / or 126s of the annular profile 122s, a clamp is provided, which is designed in the form of a stop 146s in the first line of pressure medium 28s near where it opens to chamber 34s. The sealing ring 128s can be supported axially on the stop 146s. Furthermore, in the region of the open ends of the side walls 124s and / or 126s of the annular profile 122s on the internal surfaces of the side walls 124s and / or 126s there are retaining ribs 148s and / or 150s, which extend in the peripheral direction and prevent axial movement of the sealing ring 128s out of the annular profile 122s as soon as the main sealing edges 130s and / or 132s rest on the retaining ribs 148s and / or 150s. It is evident that it is also possible to dispense with the retaining ribs 148s and / or 150s.
[0083] Figures 22a and 22b additionally show how an axial pressure of the sealing ring 128t out of the side walls 124t and / or 126t of the annular profile 122t can further be counteracted. The modality shown here differs from the example shown in figures 21a and 21b in that, on the internal surfaces of the side walls 124t and / or 126t there are ribs 152t and / or 154t, which extend in the peripheral direction and in which the collars 138t and / or 140t are positively axially supported at least in the event of an overpressure in the 34t chamber. As shown in figure 22a, necks 138t and / or 140t at normal pressure are still spaced from ribs 152t and / or 154t and come into contact with ribs 152t and / or 154t only in the event of an overpressure. It is evident that at normal pressure a contact between the 138t and / or 140t collars and the ribs 152t and / or 154t can already exist.
[0084] Figures 23a and 23b show a variation of the modality according to Figures 22a and 22b. The difference here is that the ribs 156u and / or 158u provided on the inner surfaces of the side walls 124u and / or 126u take the form of flat ribs. In this mode, in the event of an overpressure in chamber 34u, collars 138u and / or 140u are not supported in the axial direction on the flat ribs 156u and / or 158u, but are pushed in the axial direction on the flat ribs 156u and / or 158u, in so that collars 138u and 140u and / or their sealing edges 142u and 144u are pressed radially into the flat ribs 156u and / or 158u. This mode is advantageous above all when a pressure regulation has to be carried out while the vehicle is traveling. Thus, the frictional forces that arise in the event of an overpressure in chamber 34u between the sealing edges 142u and / or 144u and the flat ribs 156u and / or 158u are noticeably less than between the collars 138t and / or 140t and the ribs 152t and / or 154t according to the modality of figures 22a and 22b.
[0085] Additional modalities are shown in figures 24 to 26. These modalities are fundamentally identical to those in figures 21 to 23. One difference is, however, that the side walls 124v, 124w, 124x and / or 126v, 126w, 126x of the profiles annular 122v, 122w, 122x extend not axially, but radially. The descriptions presented with respect to figures 21 to 23, therefore, apply analogously to figures 24 to 26, with the exception that the elements and / or features that have been described here with an axial alignment must now be denoted with a radial alignment, and the elements and / or features that have been described here with a radial alignment must now be denoted with an axial alignment.
[0086] It is evident that additional variations of these modalities are conceivable. In particular, it is possible to combine additional features that are known from the previously described modalities according to Figures 3 to 17 with the modalities of Figures 21 to 26. It is therefore feasible, for example, to make the sealing ring collars larger than so that the collars protrude into the annular grooves provided on the inner surfaces of the lateral walls of the annular profile. In the event of an overpressure in the annular chamber, these collars are then pressed against the walls of the annular grooves.
[0087] Additional advantageous modalities of the described vehicle axle assemblies result from special configurations of the axle seal rings and / or seal rings that are used.
[0088] In this regard, Figures 27a and 27b again take the example of the first vehicle wheel axle assembly described according to Figures 3a and 3b. The embodiment shown in figures 27a and 27b differs from the example in figures 3a and 3b in that the two shaft sealing rings 36y and 38y each have a core 160y and / or 162y made of a material that stiffens the shaft sealing rings 36y and 38y. The 160y and 162y cores lead to a reinforcement and stabilization of the shaft sealing rings 36y and 38y, including their collars 60y and 62y, so that they can better withstand overpressure in the chamber 34y and without bending.
[0089] The cores 160y and 162y can be configured, for example, as sheet metal rings that are embedded in the material of the shaft seal rings 36y and 38y. In the illustrated example, cores 160y and 162y have an approximately L-shaped cross section, in which, in each case, a member L extends axially within the 36y and / or 38y shaft sealing ring element that adheres radially on the outside by friction fitting on hub 12y. In each case, the other member L extends in the substantially radial direction within the side of the seal ring of the shaft 36y and / or 38y facing the annular chamber 34y. The portions 164y and / or 166y the cores 160y and 162y in the region of the collars 60y and 62y follow the shape of the collars 60y and 62y and extend towards the body of the wheel axle 14y slightly obliquely towards the annular chamber 34y.
[0090] The cores 160y and 162y illustrated as an example here are of an integral construction, so that there is only a restricted mobility of the 164y and 166y portions in relation to the other portions of the 160y and 162y cores. It is, however, perfectly possible to provide a weakening of material, for example, by means of thinner material or cutouts in the transition region from the 164y and 166y portions to the neighboring portions of the 160y and 162y cores. Cores 160y and 162y can also be of a two-part construction, so that portions 164y and 166y are separated from neighboring portions of cores 160y and 162y. In this way, the articulation of portions 164y and 166y in relation to neighboring portions of cores 160y and 162y can be performed, which, in the case of an overpressure in chamber 34y, allows necks 60y and 62y, despite the reinforcement achieved, to deform more easily in order to make sealing contact with the side surface 58y of the wheel axle body 14y.
[0091] In addition, the embodiment of figures 27a and 27b differs from the example of figures 3a and 3b in that the hollow spaces 168y and 170y, which are delimited by the members extending substantially axially from the sealing rings of the shaft 36y and 38y, are used as lubricant deposits. For this purpose, the sides of the shaft sealing rings 36y and 38y remote from the annular chamber 34y are provided with covers 172y and / or 174y. The covers 172y and 174y can be designed, for example, in the form of annular spring steel sheets, which are fastened between the members extending axially from the shaft sealing rings 36y and 38y and, consequently, close to the hollow spaces 168y and 170y in an outward direction.
[0092] The dotted coils in the illustration in figures 27a and 27b indicate that the hollow spaces 168y and 170y are filled with a lubricant. In order to allow lubricant that is located in the hollow spaces 168y and 170y to reach the sealing surfaces of the shaft sealing rings 36y and 38y on the side surface 58y of the wheel axle body 14y, channels 176y and / or 178y are provided which extend out of the hollow spaces 168y and 170y in the substantially radial direction through the shaft seal ring members 36y and 38y that connect the collars 60y and 62y and the main seal edges 50y and 52y of the shaft seal rings 36y and 38y in each other. The hollow spaces 168y and 170y therefore serve as lubricant deposits, which gradually release lubricant to lubricate and cool the sealing surfaces of shaft sealing rings 36y and 38y.
[0093] Finally, in the illustrated embodiment, contrary to the example of figures 3a and 3b, two lines 180y and 182y are additionally provided, which connect the empty space 168y of the inner ring sealing ring 36y and the empty space 170y of the ring sealing of the external axial shaft 38y in each other. As is apparent, lines 180y and 182y pass through connection elements that couple the two sealing rings of shaft 36y and 38y rigidly to each other. Lines 180y and 182y allow lubricant to be transported from one of the two hollow spaces 168y and 170y to the other, so that the lubricant can be distributed in both hollow spaces 168y and 170y. If, for example, it is desired that lubricant be carried predominantly only from the shaft seal ring 38y to the shaft seal ring 36y, for example, because only the gap 170y has been previously filled with a lubricant, then if the main direction of rotation of the shaft seal rings 36y and 38y, seen in the depth of the drawings in figures 27a and 27b, extends outside the observer, lines 180y and 182y can extend obliquely against the main direction of rotation, that is, seen in the depth of the drawings of figures 27a and 27b, can come from the shaft sealing ring 38y to the shaft sealing ring 36y gradually towards the observer.
[0094] The use of caps 172y and 174y, particularly in the form of a design using annular spring steel plates, offers the additional advantage of making it possible to dispense tubular springs 54y and 56y from shaft sealing rings 36y and 38y in because the application force, which is generated by the tubular springs 54y and 56y and presses the main sealing edges 50y and 52y against the side surface 58y of the wheel axle body 14y, can alternatively be applied by the covers 172y and 174y.
[0095] A particularly advantageous embodiment is illustrated in figures 28a and 28b. The modality shown in it differs from the example in figures 27a and 27b substantially in that the two shaft sealing rings 36z and 38z have, in comparison with the shaft sealing rings 36y and 38y, an inverted mirror cross section and are locked so as not to rotate in relation to the 14z wheel axle body. Also, the first line of pressure medium 28z extends through the inner shaft seal ring 36z before opening into the annular chamber 34z. As an inner ring seal configuration 36z like this is already described in the example of figures 7a and 7b, reference can be made to the descriptions therein. The configuration of the inner shaft seal ring 36z described therein must in addition be translated analogously to the outer axial shaft seal ring 38z. The first line of pressure medium 28z in the present case extends through the lid 172z.
[0096] The resources described with reference to figures 27a and 27b must be substantially found again in the form of figures 28a and 28b, only in each case in an inverted specular form. Up to this point, reference is made to the descriptions presented pertaining to figures 27a and 27b, with the exception that the elements and / or features that were previously described with a radially external alignment now have a radially internal alignment, and the elements and / or features that have been described here with a radially internal alignment now have an radially external alignment. It is also evident that the wording referring to the wheel axle body 14y and / or the side surface 58y of the wheel axle body 14y here refers to hub 12z and / or the inner surface 80z of hub 12z.
[0097] A fundamental difference in relation to the modality according to Figures 27a and 27b is that the external shaft sealing ring 38z in the example illustrated here has no cover, so that the gap 170z in the axial direction is opened in a direction out. An arrangement like this allows the lubricant, which is located in the space of a 184z ball bearing disposed adjacent to the external shaft sealing ring 38z, to pass into the empty space 170z and, then, through channel 178z, to the sealing surfaces the shaft seal ring 38z on the inner surface 80z of the hub 12z. Likewise, the lubricant can pass out of the ball bearing 184z through lines 180z and 182z to the empty space 168z of the inner ring seal ring 36z and, from there, through channel 176z, to the sealing surfaces of the ring shaft seal 36z on inner surface 80z of hub 12z.
[0098] It is evident that, in this mode as well, the shaft sealing ring 38z can be equipped with a cover that closes the gap 170z in order to form a lubricant tank in the gap 170z. It is also conceivable to mount a cover like this, but provide it with one or more through-openings that allow the lubricant of the 184z ball bearing to additionally enter the 170z void.
[0099] A situation like this is represented in the example of figures 29a and 29b. The cap 174za shown here is provided with a through opening, through which lubricant located in the ball bearing 184za can enter the empty space 170za. The 174za cap, therefore, has substantially the design purpose of making the 56za tubular spring of the 38za shaft seal ring dispensable, due to the application force that presses the main sealing lip 52za against the inner surface 80za of the 12za hub can be applied by the 174za cover. It is therefore possible to dispense with the 56za tubular spring.
[00100] Apart from this aspect, the modality of figures 29a and 29b differs from the example of figures 28a and 28b also in that the two sealing rings of the shaft 36za and 38za are fused as a unit and the two hollow spaces 168za and 170za are connected each other only by a single 180za line. The 180za line here passes through the portion connecting the two shaft seal rings 36za and 38za to each other.
[00101] The example of figures 29a and 29b further differs from the example of figures 28a and 28b substantially in that, in the hollow spaces 168za and 170za, there are sponge foam materials 179za and / or 181za, which fill part of the hollow spaces 168za and 170za and cover the entrance openings of channels 176za and 178za. The 179za and / or 181za foam materials have closing surfaces, which extend in the axial direction and which are located radially above the 180za line inlet and / or outlet openings. Lubricant located in the foam-free parts of the 168za and 170za hollow spaces can therefore flow unimpeded through the 180za line. The 179za and / or 181za foam materials ensure that lubricant located in the hollow spaces 168za and 170za does not flow out directly through channels 176za and 178za, but is first absorbed by the foam materials 179za and / or 181za and stored before being gradually released in channels 176za and 178za. In the illustrated example, channels 176za and 178za are also filled with sponge-like foam materials, however this is not absolutely necessary. 183za and / or 185za sponge foam materials are furthermore arranged in the spaces between collars 60za and 62za and / or their sealing edges 64za and 66za, the main sealing edges 50za and 52za and the hub 12za. Lubricant that passes out of hollow spaces 168za and 170za through channels 176za and 178za into these intermediate spaces is absorbed by foam materials 183za and / or 185za and then distributed evenly on the sealing surfaces of the 36za shaft sealing rings and 38za on the inner surface 80za of the cube 12za.
[00102] It is clear to those skilled in the art that the features described with reference to figures 27 to 29 can be combined in any desired manner with each other and are also equally applicable to other embodiments of the vehicle wheel axle assembly described. It is therefore feasible, for example, in the modalities described with reference to figures 3 to 20, to also provide corresponding reinforcements in the shaft sealing rings or to equip the shaft sealing rings with lubricant deposits and / or sponge-like foam materials in the hollow spaces.
[00103] The modalities shown in figures 28 and 29 are particularly advantageous in situations where, for spatial reasons, design limits are imposed on the vehicle wheel axle assembly. For example, it may be that the material thickness of the wheel axle body is not sufficient to pass the first line of pressure medium. The illustrated modalities avoid this problem in that they allow the first line of pressure medium 28z and / or 28za to pass through the sealing ring of the axis 36z and / or 36za into the annular chamber 34z and / or 34za. As the collars 60z and 62z and / or 60za and 62za of both shaft seal rings 36z and 38z and / or 36za and 38za are arranged radially on the outside, these arrangements deal with minimal axial spatial requirements. When pressure is fed through the first line of pressure medium 28z and / or 28za, the collars 60z and 62z and / or 60za and 62za are namely pressed out of each other by virtue of the admission of the pressure medium being made by the annular chamber 34z and / or 34za. The two shaft sealing rings 36z and 38z and / or 36za and 38za can therefore easily be arranged so closely adjacent to each other that their necklaces 60z and 62z and / or 60za and 62za are in mutual contact when normal pressure prevails in the 34z and / or 34za chamber.
[00104] Figures 30 to 32, whose description now follows, again occupy the vehicle wheel axle set, which is enough with only sealing ring and extends the modalities of figures 21 to 26 in the sense of the resources described above with reference to the figures 27 and 29.
[00105] Figures 30a and 30b extend the modality of figures 21a and 21b. This example differs from the example of figures 21a and 21b in that the sealing ring 128zb has a core 186zb made of a material that stiffens the sealing ring 128zb. The 186zb core stiffens and stabilizes the 128zb sealing ring, including its 138zb and 140zb collars, so that they can better withstand overpressure in the 34zb chamber.
[00106] The 186zb core can be designed, for example, by means of a sheet metal ring that is embedded in the material of the 128zb seal ring. In the illustrated example, the core 186zb extends substantially parallel to the side of the sealing ring 128zb facing the annular chamber 34zb. The 188zb and / or 190zb portions of the 186zb core in the region of the necklaces 138zb and 140zb follow the shape of the necklaces 138zb and 140zb and extend towards the side walls 124zb and 126zb of the annular profile 122zb slightly towards the annular chamber 34zb.
[00107] The 186zb core shown here as an example is of an integral construction, so that there is only restricted mobility of the 188zb and 190zb portions in relation to the neighboring 186zb core portions. It is, however, perfectly possible to provide in each case a weakening of material, for example, using thinner material or providing cutouts, in the region of the transition from the 188zb and 190zb portions to the neighboring portions of the 186zb core. The 186zb core can also be of a three-part construction, so that the 188zb and 190zb portions are separated from the neighboring 186zb core portions. In this way, an articulation of the 188zb and 190zb portions in relation to the neighboring portions of the 186zb core can be designed, in which case an overpressure in the 34zb chamber allows the necks 138zb and 140zb, despite the reinforcement, to deform more easily in order to enter in sealing contact with the side walls 124zb and 126zb of the annular profile 122zb.
[00108] The embodiment of figures 30a and 30b further differs from that of figures 21a and 21b in that the void 192zb that is formed by the substantially axial extending members of the sealing ring 128zb is used as a lubricant tank. For this purpose, the remote 128zb sealing ring sides of the 34zb annular chamber are provided with a 194zb cap. The cover 194zb can be designed, for example, in the form of an annular spring steel plate, which is secured between the axially extending members of the sealing ring 128zb and consequently closes the void 192zb in an outward direction. The first line of pressure medium 28zb then extends through the cap 194zb. It is evident that, given an arrangement like this, it is also possible to dispense tubular springs 134zb and 136zb from the sealing ring 128zb, due to the application force, which is generated by the tubular springs 134zb and 136zb and presses on the main sealing edges 130zb and 132zb against the side walls 124zb and 126zb of the annular profile 122zb, can alternatively be applied by the cover 194zb.
[00109] The dotted coils in the representation of figures 30a and 30b indicate that the empty space 192zb is filled with a lubricant. In order that the lubricant located in the empty space 192zb can reach the sealing surfaces of the sealing ring 128zb on the side walls 124zb and 126zb of the annular profile 122zb, channels 196zb and / or 198zb are provided that extend out of the empty space 192zb in substantially radial direction through the members of the sealing ring 128zb connecting the collars 138zb and 140zb and the main sealing edges 130zb and 132zb of the sealing ring 128zb to each other. The 192zb void therefore serves as a lubricant tank, which gradually releases lubricant to lubricate and cool the sealing surfaces of the 128zb sealing ring through channels 196zb and 198zb.
[00110] What the modalities of figures 21 to 26 and 30 have in common is that the annular chamber is formed in each case within the side walls of the annular profile that is connected to the cube. It is evident from the figures that a seal between the body of the wheel axle and the hub is not guaranteed by the ring profile alone. In order to prevent dirt or dust particles from entering a ball bearing disposed adjacent to the annular profile and to prevent lubricant from escaping from the ball bearing, additional shaft seal rings can be disposed axially inside or axially outside the annular profile.
[00111] A possible modality, in which the assembly of additional shaft seal rings can be avoided, is shown in figures 31a and 31b. The example shown is similar to the modality of figures 30a and 30b and differs only in that the radially internal side wall 126zc of the annular profile 122zc is smaller than the radially external side wall 124zc, so that the radially internal main seal edge 132zc of the ring sealing ring is in contact with the wheel axle body 14zc. The main sealing lip 132zc is pressed against the wheel axle body 14zc by the application force generated by the tubular spring 136zc and / or the cap 194zc and therefore makes a seal between the body of the wheel axle 14zc and the hub 12zc . By rotating the hub 12zc around the wheel axle body 14zc, the main sealing lip 132zc slides over the side surface 58zc of the wheel axle body 14zc. It is evident that the empty space 192zc formed by the sealing ring 128zc in this case does not need to be filled with lubricant, because the lubricant that is located in the space of a ball bearing 200zc disposed adjacent to the annular profile 122zc can pass into the empty space 192zc before being then distributed to the sealing surfaces of the 128zc sealing ring.
[00112] Figures 32a and 32b finally show a development of the modality of figures 31a and 31b. This example differs from the previous example in that in the 192zd void there is a 202zd sponge-like foam material that fills part of the 192zd void and overlaps the 196zd and 198zd channels. The 202zd foam material has a radially extending closing surface and basically ensures that lubricant located in the empty space area without 192zd foam material cannot flow out unimpededly through channels 196zd and 198zd, but is first absorbed by 202zd foam material and stored before it is then gradually released into channels 196zd and 198zd. In the illustrated modality, the channels 196zd and 198zd are also filled with sponge-like foam material, however this is not absolutely necessary. 204zd and 206zd sponge foam materials are furthermore arranged in the intermediate spaces between the 138zd and / or 140zd collars, the main sealing edges 130zd and / or 132zd and the side walls 124zd and 126zd of the 122zd annular profile. Lubricant that passes out of the 192zd void through channels 196zd and 198zd into these intermediate spaces is absorbed by the foam materials 204zd and 206zd and then evenly distributed through them on the sealing surfaces of the 128zd sealing ring on the side walls 124zd and 126zd of the annular profile 122zd.
[00113] It is clear to those skilled in the art that the features described with reference to figures 30 to 32 are equally applicable to other modalities of the vehicle wheel axle set described. For the modalities of figures 22 and 23, too, it is therefore possible to provide reinforcements in the sealing rings or to equip the sealing rings with deposits of lubricant and sponge-like material in the hollow spaces thereof. The same applies to the modalities of figures 24 to 26, with the exception that the elements and / or features that were described here with an axial alignment must now be denoted with a radial alignment, and the elements and / or features that were here described with a radial alignment and are now denoted with an axial alignment.

权利要求:
Claims (35)
[0001]
1. Vehicle wheel axle assembly (10) comprising a hub (12; 12a - 12r; 12y; 12z; 12za), which is mounted on a cylindrical wheel axle body (14; 14a - 14r; 14y; 14z ; 14za) so that it can rotate around a central longitudinal geometry axis (A), and an inner axial shaft sealing ring (36; 36a - 36q; 114r; 36y; 36z; 36za) and a sealing ring of the external axial axle (38; 38a - 38o; 112p; 112q; 118r; 38y; 38z; 38za) for indirect or direct sealing between the wheel axle body (14; 14a - 14r; 14y; 14z; 14za) and the hub (12 '12a - 12r; 12y; 12z; 12za) comprising - an annular chamber (34; 34a - 34r; 34y; 34z; 34za) which is formed between the two axle sealing rings, the body of the wheel axle (14; 14a - 14r; 14y; 14z; 14za) and the cube (12; 12a - 12r; 12y; 12z; 12za); - a first line of pressure medium (28; 28a - 28r; 28y; 28z; 28za) which extends through the wheel axle body (14; 14a - 14r; 14y; 14z; 14za) or one of the two rings of shaft seal and opens to the annular chamber (34; 34a - 34r; 34y; 34z; 34za); and - a second line of pressure medium (40; 40a - 40r; 40y; 40z; 40za) extending out of the annular chamber (34; 34a - 34r; 34y; 34z; 34za) through the hub (12; 12a - 12r; 12y; 12z; 12za) and is designed to be connected to a wheel that is attached to the hub (12; 12a - 12r; 12y; 12z; 12za), in which at least one of the shaft sealing rings adjacent to the annular chamber (34; 34a - 34r; 34y; 34z; 34za) is provided radially inside or radially outside with a collar (60a - 60g; 60l - 60o; 60y; 60z; 60za, 62a - 62d; 62l - 62o; 62y; 62z; 62za), characterized by the fact that at least one of the shaft sealing rings (36y; 36z; 36za, 38y; 38z; 38za) has at least one channel (176y; 176z; 176za, 178y; 178z; 178za) , which extends outside an internal void (168y; 168z; 168za, 170y; 170z; 170za) of the shaft seal ring (36y; 36z; 36za, 38y; 38z; 38za) in the radial direction to a side portion the shaft seal ring (36y; 36z; 36za, 38y; 38z; 38za) which is located in a region between the necklace (60y; 60z; 60za, 62y; 62z; 62za) and a main sealing lip (50y; 50z; 50za, 52y; 52z; 52za) of the shaft sealing ring (36y; 36z; 36za, 38y; 38z; 38za).
[0002]
2. Vehicle wheel axle assembly according to claim 1, characterized in that the collar (60a; 60b; 60e; 60n; 60o; 60y; 60z; 60za, 62a; 62b; 62n; 62o; 62y; 62z; 62za) has a sealing lip (64a; 64b; 64e; 64n; 64o; 64y; 64z; 64za, 66a; 66b; 66n; 66o; 66y; 66z; 66za), which at least in the case of an overpressure in the chamber (34a; 34b; 34e; 34n; 34o; 34y; 34z; 34za) is in contact with the wheel axle body (14a; 14b; 14e; 14n; 14o; 14y; 14z; 14za) and / or the hub (12a; 12b; 12e; 12n; 12o; 12y; 12z; 12za).
[0003]
Vehicle wheel axle assembly according to claim 1, characterized in that, on the side surface (58c) of the wheel axle body (14c) opposite to a radially internal collar (60c, 62c) there is a annular groove (72c, 74c), into which the collar (60c, 62c) protrudes radially.
[0004]
4. Vehicle wheel axle assembly according to either of Claims 1 or 3, characterized in that a groove on an inner surface (80f) of the hub (12f) opposite to a radially external collar (60f) ring (72f), into which the collar (60f) protrudes radially.
[0005]
5. Vehicle wheel axle assembly according to claim 1, characterized in that, on the lateral surface (58d; 58l; 58m) of the wheel axle body (14d; 14l; 14m) there is a rib (76d ; 76l; 76m, 78d; 78l; 78m), which extends in the peripheral direction and in which a radially internal collar (60d; 60l; 60m, 62d; 62l; 62m) is axially supported at least in the case of overpressure in the chamber (34d; 34l; 34m).
[0006]
6. Vehicle wheel axle assembly according to either of claims 1 or 5, characterized in that, on an internal surface (80g) of the hub (12g) there is a rib (76g), which extends in the direction peripheral and in which a radially external collar (60g) is axially supported at least in the case of overpressure in the chamber (34g).
[0007]
Vehicle wheel axle assembly according to either claim 5 or claim 6, characterized in that the rib (76d; 76g; 76l; 76m, 78d; 78g; 78l; 78m) is integrally formed with the body the wheel axle (14d; 14l; 14m) or the hub (12g).
[0008]
Vehicle wheel axle assembly according to either of claims 5 or 6, characterized in that the rib (76d; 76g; 76l; 76m, 78d; 78g; 78l; 78m) is formed by a ring or O-RING that is inserted into a slot.
[0009]
Vehicle wheel axle assembly according to any one of claims 5 to 8, characterized in that the rib has a rectangular cross section.
[0010]
Vehicle wheel axle assembly according to any one of claims 5 to 9, characterized in that a radially internal collar (60d; 60l; 60m, 62d; 62l; 62m) has a sealing lip, which, at least in the case of an overpressure in the chamber (34d; 34l; 34m), it is in contact with the wheel axle body (14d; 14l; 14m) or the rib (76d; 76l; 76m, 78d; 78l; 78m) , and / or a radially external collar (60g) has a sealing lip, which, at least in the case of an overpressure in the chamber (34g), is in contact with the hub (12g) or the rib (76g).
[0011]
Vehicle wheel axle assembly according to any one of claims 1 to 10, characterized in that, between the two axle sealing rings (36h; 36i, 38h; 38i) on the side surface (58h; 58i ) of the wheel axle body (14h; 14i), an annular flange (84h; 84i) with two flexible radial side walls (86h; 86i, 88h; 88i) is mounted, on which the first line of pressure medium (28h ; 28i) opens on the annular flange (84h; 84i) between the two side walls (86h; 86i, 88h; 88i) inside the annular chamber (34h; 34i).
[0012]
Vehicle wheel axle assembly according to claim 11, characterized in that, on an internal surface (80i) of the hub (12i) opposite the annular flange (84i), a ring (90i) with a section U-shaped cross section is attached, whose side walls (92i, 94i) are directed radially inward, and the second line of pressure medium (40i) extends through the ring (90i) between its side walls (92i, 94i) inside the hub (12i).
[0013]
13. Vehicle wheel axle assembly according to any one of claims 1 to 12, characterized in that the two axle sealing rings (36j; 36l; 36o; 36y; 36z; 36za, 38j, 38l; 38o ; 38y; 38z; 38za) are axially rigidly coupled together.
[0014]
14. Vehicle wheel axle assembly according to any one of claims 1 to 13, characterized in that the two axle sealing rings (36k; 36m; 36n; 36o, 38k; 38m; 38n; 38o) are axially flexibly coupled together.
[0015]
15. Vehicle wheel axle assembly according to any one of claims 1 to 14, characterized in that at least one of the two axle sealing rings (114r, 112p; 112q; 118r) is integrated into a bearing. spheres (104p; 104q; 104r, 116r), which is disposed between the wheel axle body (14p; 14q; 14r) and the hub (12p; 12q; 12r).
[0016]
Vehicle wheel axle assembly according to any one of claims 1 to 15, characterized in that a valve is provided for pressure relief of the annular chamber (34; 34a - 34r; 34y; 34z; 34za).
[0017]
17. Vehicle wheel axle assembly according to any one of claims 1 to 16, characterized in that at least one of the axle sealing rings (36y; 36z; 36za, 38y; 38z; 38za), particularly in collar region (60y; 60z; 60za, 62y; 62z; 62za), has a core (160y; 160z, 162y; 162z) made of a material that stiffens the shaft sealing ring (36y; 36z; 36za, 38y; 38z; 38za).
[0018]
18. Vehicle wheel axle assembly according to claim 17, characterized in that a portion (164y; 164z, 166y; 166z) of the core (160y; 160z, 162y; 162z) that is arranged in the collar region (60y; 60z; 60za, 62y; 62z; 62za) is pivotable in relation to the rest of the core (160y; 160z, 162y; 162z).
[0019]
19. Vehicle wheel axle assembly according to claim 1, characterized in that the empty space (168y; 168z; 168za, 170y; 170z; 170za) on the side of the axle seal ring (36y; 36z; 36za, 38y; 38z; 38za) remote from the annular chamber (34y; 34z; 34za) is provided with a cover (172y; 172z; 174y; 174za).
[0020]
20. Vehicle wheel axle assembly according to claim 19, characterized in that the empty space (168y; 168z; 168za, 170y; 170z; 170za) is filled with a lubricant.
[0021]
21. Vehicle wheel axle assembly according to any one of claims 1 to 20, characterized in that in the empty space (168za, 170za) there is a sponge-like foam material (179za, 181za), which fills at least part of the empty space (168za, 170za) and overlaps an entrance opening of at least one channel (176za, 178za).
[0022]
22. Vehicle wheel axle assembly according to any one of claims 1 to 21, characterized in that an intermediate space between the collar (60za, 62za) and the main sealing lip (50za, 52za) is filled by the least partially with a sponge-like foam material (183za, 185za).
[0023]
23. Vehicle wheel axle assembly according to any one of claims 1 to 22, characterized in that an internal void space (168y; 168z; 168za) of the inner axial shaft seal ring (36y; 36z; 36za) ) and an internal void (170y; 170z; 170za) of the outer axial shaft seal ring (38y; 38z; 38za) are connected to each other by at least one line (180y; 180z; 180za, 182y; 182z).
[0024]
24. Vehicle wheel axle assembly according to claim 23, characterized in that the line (180y; 180z; 180za, 182y; 182z) ascends radially from an axle seal ring (36y; 36z; 36za, 38y; 38z; 38za) towards the other shaft seal ring (36y; 36z; 36za, 38y; 38z; 38za) and / or extends obliquely against a main direction of rotation of the hub (12y; 12z; 12za) .
[0025]
25. Vehicle wheel axle assembly (10) comprising a hub (12s - 12x; 12zb - 12zd), which is mounted on a cylindrical wheel axle body (14s - 14x; 14zb - 14zd) so that it can rotate about a central longitudinal geometric axis (A), comprising:
[0026]
26. Vehicle wheel axle assembly according to claim 25, characterized in that the annular profile (122s - 122x; 122zb - 122zd) is integrally formed, in particular cast, with the hub (12s - 12x; 12zb - 12zd) .An annular profile (122s - 122x; 122zb - 122zd) with a U-shaped cross section, which is connected to an inner surface (80s - 80x; 80zb - 80zd) of the hub (12s - 12x; 12zb - 12zd) and whose side walls (124s - 124x; 124zb - 124zd, 126s - 126x; 126zb - 126zd) extend axially or radially;
[0027]
27. Vehicle wheel axle assembly according to either of claims 25 or 26, characterized in that a clamp (146s; 146v, 148s; 148v, 150s; 150v) is provided, which, in the case of a profile ring (122s - 122u) with axially extending side walls (124s - 124u, 126s - 126u), fix the axial position of the sealing ring (128s - 128u) and, in the case of an annular profile (122v - 122x) with radially extending side walls (124v - 124x, 126v - 126x), fix the radial position of the sealing ring (128v - 128x) .a sealing ring (128s - 128x; 128zb - 128zd), which is arranged between the walls lateral (124s - 124x; 124zb - 124zd, 126s - 126x; 126zb - 126zd), is locked so as not to rotate in relation to the wheel axle body (14s - 14x; 14zb - 14zd) and, in the annular profile (122s - 122x ; 122zb - 122zd), delimits an annular chamber (34s - 34x; 34zb - 34zd);
[0028]
28. Vehicle wheel axle assembly according to any one of claims 25 to 27, characterized in that, in the case of an annular profile (122s - 122u; 122zb - 122zd) with axially extending side walls (124s - 124u; 124zb - 124zd, 126s - 126u; 126zb - 126zd), the sealing ring (128s - 128u; 128zb - 128zd) adjacent to the annular chamber (34s - 34u; 34zb - 34zd) is provided radially inside and radially outside with a collar (138s - 138u; 138zb - 138zd, 140s - 140u; 140zb - 140zd), and which, in the case of an annular profile (122v - 122x) with radially extending side walls (124v - 124x, 126v - 126x) , the sealing ring (128v - 128x) adjacent to the annular chamber (34v - 34x) is provided axially inside and axially outside with a collar (138v - 138x, 140v - 140x). a first line of pressure medium (28s - 28x ; 28zb - 28zd), which extends through the sealing ring (128s - 128x; 128zb - 128zd) and opens to the annular chamber (34s - 34x; 34zb - 34zd); and
[0029]
29. Vehicle wheel axle assembly according to claim 28, characterized in that, in the case of an annular profile (122t) with axially extending side walls (124t, 126t), it exists on the side walls (124t , 126t) of the annular profile (122t) a support structure (152t, 154t), in which the radially inner and radially outer collar (138t, 140t) are axially supported at least in the case of overpressure in the chamber (34t), and that, in the case of an annular profile (122w) with radially extending side walls (124w, 126w), there is on the side walls (124w, 126w) of the annular profile (122w) a support structure (152w, 154w), in which the axially internal and external axial collars (138w, 140w) are radially supported at least in the case of an overpressure in the chamber (34w). a second line of pressure medium (40s - 40x; 40zb - 40zd), extending out of the annular chamber (34s - 34x; 34zb - 34zd) through the annular profile (122s - 122x; 122zb - 122 zd) and the cube (12s - 12x; 12zb - 12zd) and is designed to be connected to a wheel that is attached to the hub (12s - 12x; 12zb - 12zd), characterized by the fact that the sealing ring (128zb - 128zd) has at least one channel (196zb; 196zd, 198zb; 198zd), which extends outside an internal void space (192zb - 192zd) of the seal ring (128zb - 128zd), in the case of an annular profile (122zb - 122zd) with axially extending side walls (124zb - 124zd, 126zb - 126zd) in the radial direction and, in the case of an annular profile with side walls extending radially in the axial direction to a lateral portion of the seal ring (128zb - 128zd) which is located in a region between a collar (138zb; 138zd, 140zb; 140zd) and a main sealing lip (130zb; 130zd, 132zb - 132zd) of the sealing ring (128zb - 128zd).
[0030]
30. Vehicle wheel axle assembly according to either of claims 28 or 29, characterized in that the sealing ring (128zb - 128zd), particularly in the region of at least one of the two collars (138zb; 138zd, 140zb; 140zd) has a core (186zb) made of a material that stiffens the sealing ring (128zb - 128zd).
[0031]
31. Vehicle wheel axle assembly according to claim 30, characterized in that a portion (188zb, 190zb) of the core (186zb) which is arranged in the region of a collar (138zb; 138zd, 140zb; 140zd) it is pivotable in relation to the rest of the core (186zb).
[0032]
32. Vehicle wheel axle assembly according to claim 25, characterized in that the empty space (192zb - 192zd) on the side of the sealing ring (128zb - 128zd) remote from the annular chamber (34zb - 34zd) is provided with a cover (194zb; 194zc).
[0033]
33. Vehicle wheel axle assembly according to claim 32, characterized in that the empty space (192zb - 192zd) is filled with a lubricant.
[0034]
34. Vehicle wheel axle assembly according to any one of claims 25 to 33, characterized in that in the empty space (192zd) there is a sponge-like foam material (202zd), which fills at least part of the empty space (192zd) and overlaps an opening of at least one channel (196zd, 198zd).
[0035]
35. Vehicle wheel axle assembly according to any one of claims 25 to 34, characterized in that an intermediate space between the collar (138zd, 140zd) and the main sealing lip (130zd, 132zd) is filled by least partially with a sponge-like foam material (204zd, 206zd).

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同族专利:

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公开号 | 公开日

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BR112015009215A2|2017-07-04|

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WO2014063873A3|2014-08-07|

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US20150290986A1|2015-10-15|

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EP2911895B1|2016-11-23|

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CA2888735C|2020-07-14|

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EP2911895A2|2015-09-02|

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WO2014063873A2|2014-05-01|

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AU2013336975B2|2017-06-29|

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US9604509B2|2017-03-28|

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CA2888735A1|2014-05-01|

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AU2013336975A1|2015-05-14|

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法律状态:
2018-11-21| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|

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2019-11-19| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|

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2020-07-07| B06A| Notification to applicant to reply to the report for non-patentability or inadequacy of the application [chapter 6.1 patent gazette]|

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2020-10-27| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|

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2021-01-05| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 20/09/2013, OBSERVADAS AS CONDICOES LEGAIS. |

优先权:

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申请号 | 申请日 | 专利标题

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DE102012021044.2A|DE102012021044B4|2012-10-26|2012-10-26|Vehicle axle assembly with integrated pressure medium line for tire filling|

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DE102012021044.2|2012-10-26|

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DE102013003562.7|2013-03-01|

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DE201310003562|DE102013003562A1|2013-03-01|2013-03-01|Vehicle axle assembly has annular chamber that is formed between two shaft sealing rings, axle body and hub by pressure medium line which extends through axle body or through one of two shaft sealing rings|

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PCT/EP2013/069599|WO2014063873A2|2012-10-26|2013-09-20|Vehicle axle assembly comprising integrated pressure medium line for filling tyres|

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