DE102017127432A1 - Sealing arrangement for a rotary feedthrough of a wheel bearing of a motor vehicle - Google Patents

Abstract

It is a sealing arrangement (24) for a wheel bearing (12) of a motor vehicle, in particular a truck, provided with a sealing partner (50) rotatable about an axis of rotation (48), arranged substantially coaxially with the axis of rotation (48) and relative to the sealing partner (50) rotatable sealing unit (38) for producing a sealing contact with the sealing partner (50), wherein the sealing unit (38) for changing a contact pressure on the sealing partner (50) relative to the sealing partner (50) displaceable and / or elastically deformable configured wherein the sealing partner (50) is elastically supported on a rear side facing away from the sealing unit (38). Due to the flexible in the pressing direction of the sealing unit (36) yielding sealing partner (50), a sufficient sealing effect can be achieved over a designated pressure range at the lowest possible contact force, so that at a low wear a good sealing effect in a rotary feedthrough (10) for a Wheel bearing (12) is possible.

Description

The invention relates to a sealing arrangement for a rotary feedthrough of a wheel bearing of a motor vehicle, with the aid of a rotary feedthrough can be formed in the wheel bearing to pass in the radial direction, a pressurized fluid through the wheel bearing, in particular to adjust a tire pressure of a tire of the motor vehicle.

The tires of motor vehicles have different, optimal tire pressure depending on the surface and load. For example, in loose ground, sand, mud or the like, the best possible traction is needed, which can be achieved with a tire with a very low tire pressure. On a level surface such as a country road, even with a higher tire pressure, sufficient traction is achieved, with a tire having a high tire pressure resulting in less friction and lower fuel consumption. For a fully loaded truck, the optimal tire pressure is higher than for a no-load ride. Trucks that drive in the field or on construction sites, such as a dump truck, are usually either completely empty or completely loaded on the way, so that in particular for such trucks, the difference between the optimal tire pressures is particularly large.

Out DE 10 2015 212 641 A1 a sealing arrangement for a wheel bearing of a motor vehicle is known in which the sealing arrangement has a limited by axially displaceable sealing elements pressure chamber for the passage of compressed air in the radial direction, wherein the sealing elements are pressed by the pressure of the compressed air against each a relatively rotatable ring member of the wheel bearing to to make a sealing contact. With the aid of such a wheel bearing, a pneumatic system provided in the motor vehicle can adapt the tire pressure of the motor vehicle to the optimum tire pressure in the current situation.

There is a constant need for low wear to achieve a good sealing effect in a rotary feedthrough for a wheel bearing.

It is the object of the invention to show measures that allow for a low wear a good sealing effect in a rotary feedthrough for a wheel bearing.

The object is achieved according to the invention by a sealing arrangement having the features of claim 1. Preferred embodiments of the invention are specified in the subclaims and the following description, which individually or in combination may constitute an aspect of the invention.

According to the invention, a sealing arrangement is provided for a wheel bearing of a motor vehicle, in particular a truck, with a sealing partner rotatable about an axis of rotation, a sealing unit arranged substantially coaxially with the axis of rotation and rotatable relative to the sealing partner for producing a sealing contact with the sealing partner, the sealing unit being modified a contact force on the sealing partner relative to the sealing partner displaceable and / or elastically deformable configured, wherein the sealing partner is elastically supported on a side facing away from the sealing unit rear side.

The sealing unit can in particular be displaced from a pressure provided by a pressure source to the sealing partner. For this purpose, the sealing unit can be moved toward the sealing partner and / or elastically deformed by the applied pressure on the sealing partner. A side facing away from the sealing partner back of the sealing unit can point to a pressure chamber, which can be filled by a pressure fluid coming from the pressure source, in particular compressed air, when the pressure fluid from the pressure source to a pressure space, in particular a tire tube of a motor vehicle tire, flows. The contact pressure of the sealing unit on the sealing partner can thereby depend on the currently applied to the back of the seal unit pressure. This results in a lower pressure at a lower contact pressure and at a higher pressure to a higher contact pressure. At a low pressure, the lower pressing force may be sufficient to cause a sufficient sealing effect between the sealing unit and the sealing partner to avoid unnecessary leakage, at the same time the contact pressure is so low that an abrasive wear between the seal unit and the sealing partner, relative to each other can rotate, can be kept low. At a higher pressure, a higher contact pressure can automatically set, which is sufficient even at the higher pressure to prevent leakage between the seal unit and the sealing partner through. Since the sealing unit, in particular due to the materials used, can be designed optimized for a good sealing effect, under a rising pressure a disproportionate increase in contact pressure may already be sufficient to bring about a sufficient sealing effect even at a higher pressure.

Due to the elastic support of the sealing partner on its back, the sealing partner with a rising contact pressure of the sealing unit of the sealing unit something spring away. This results in a slightly displaced in the contact position a force equilibrium between the force applied by the sealing unit contact force and the force applied by the sealing partner counterforce, which can be based on a lower contact pressure. If the sealing unit is made of an elastomeric material and is elastically deformed by the pressure applied to its back to the sealing partner, due to the elastic support of the sealing partner, a correspondingly greater elastic deformation of the sealing unit is required, resulting in a higher resistance of the sealing unit against the elastic deformation and a correspondingly lower arriving at the sealing element contact pressure leads. The pressure force applied to the sealing partner at a higher pressure from the sealing unit can thus be so high that leakage can be avoided, while at the same time the contact pressure can be kept at such a low level that unnecessary abrasive wear can be avoided. For this purpose, the spring properties of the sealing partner and the spring properties of the sealing unit can be suitably matched to one another. The spring characteristics of the sealing unit and the elastic support of the sealing partner can be coordinated with one another such that the contact force between the sealing unit and the sealing partner lies as close as possible above the minimum sealing effect provided for the respective pressure over an expected pressure range of the pressure fluid. Wear of the seal assembly can be minimized and the life can be increased. Due to the flexible in the pressing direction of the sealing unit resilient sealing partner, a sufficient sealing effect can be achieved over a designated pressure range at the lowest possible contact pressure, so that with a low wear a good sealing effect in a rotary feedthrough for a wheel bearing is possible.

The sealing unit may be accommodated in a seal holder relatively movable but co-rotating. The seal holder may be rotatably connected to an inner ring of the wheel bearing, while the sealing partner is rotatably connected to an outer ring of the wheel bearing, or vice versa. Due to the sealing contact of the sealing unit to the sealing partner, a seal of the inner ring relative to the outer ring can be done. The at least one material used for the sealing unit is in particular heat-resistant up to a temperature of for example 260 ° C. In particular, the material has a ductility which is sufficient to be insensitive to shocks expected during operation. For example, the respective material has an elongation of 5% to 10%. The thermal expansion coefficient of the respective material corresponds in particular essentially to the thermal expansion coefficient of the material used for the bearing rings of the wheel bearing, in particular steel. In particular, the sealing unit has a support ring, which can be directly attached to the sealing partner, for removing at least a large part of the contact forces and / or a sealing ring which can be applied directly to the sealing partner to provide a sealing contact with the sealing partner by elastic deformation. The support ring and / or the sealing ring can be used in particular in a, preferably made of an elastomeric material, retaining ring of the sealing unit. The retaining ring can be elastically deformed, for example, by the pressure applied in the pressure chamber and press the support ring and / or the sealing ring against the sealing partner, while the support ring and / or the sealing ring can be made of a different material. In particular, the support ring is made of a particularly pressure-resistant and / or wear-resistant material. For example, the support ring is made of a polyamide-imide (PAI), which may have an increased graphite content for improved wear resistance. The sealing ring can be particularly soft and thereby achieve a particularly good seal. The sealing ring is made of polytetrafluoroethylene (PTFE), for example. The support ring can remove a large part of the contact forces, so that acting on the sealing ring lower forces and not as easily wear in comparison to the support ring softer material of the sealing ring. When the retaining ring is made of an elastomeric material, the sealing unit during assembly can be easily pressed through a to the Dcihtpartner facing tapered opening of the seal holder to retain the seal unit until the assembly of the sealing partner captive in the seal holder. Alternatively, the sealing partner facing the opening of the seal holder in the radial direction be as large as the radial extent of the seal unit, in particular between the seal holder and the seal unit a clearance is formed, which allows easy axial displacement of the seal unit in the seal holder.

The sealing unit may be provided for sealing in a first direction, wherein a seal unit symmetric, mirror image and / or analog configured further sealing unit may be provided for sealing in a direction opposite to the first direction of the second direction. In particular, the pressure of the pressure fluid can rest between the sealing unit and the further sealing unit in order to press the sealing unit and the further sealing unit away from one another against the respective sealing partner. The sealing partner provided for the further sealing unit can likewise be symmetrical, mirror-image and / or analogous to that for the sealing unit provided sealing partners be designed and in particular also be resiliently supported.

In particular, the sealing partner has on its rear side, in particular made of an elastomeric material, spring element. The spring element can be supported and / or fixed on one side to the sealing partner and on the other side to a component rotating relative to the sealing unit, in particular a bearing ring of the wheel bearing. The spring element may be configured, for example, as a plate spring. Preferably, the spring element is made of an elastomeric body, which is molded in particular on the sealing partner and the supporting component. As a result, in addition, a rotationally fixed connection of the sealing partner can be achieved with the supporting member, which is preferably somewhat torsionally elastic in the circumferential direction.

The spring element preferably has a higher spring constant below a predefined limit spring force than above the limit spring force. Until the contact force has reached the predefined limit spring force, the sealing partner does not spring or only slightly away. Only when the predefined limiting spring force is reached by the contact force, the sealing partner can spring away. With an increasing pressure of the pressurized fluid, the contact pressure can increase substantially proportionally until at the predefined limiting spring force a contact force sufficient for the expected pressure range is achieved, which no longer needs to be increased further, and then at least more strongly deflecting the sealing partner at this point Pressing force is maintained.

Particularly preferably, the spring element at least partially on a progressive spring characteristic. As a result, even with the expected pressure range of the pressure fluid exceeding sudden pressure peaks leakage can be avoided with a correspondingly high contact pressure. A striking of the sealing partner on another component, when the maximum compressibility of the spring element is achieved, can be avoided. In addition, it can be avoided that the spring element is overloaded at a sudden pressure peak and retains a permanent plastic deformation, which can adversely affect the sealing effect.

In particular, the sealing unit is received in a seal holder relatively movable and / or elastically deformable, wherein the seal holder has a limit stop for limiting a maximum relative mobility and / or elastic deformability of the sealing unit relative to the sealing partner. Thereby, the displacement of the seal unit and a maximum contact force can be limited. Damage to the sealing partner and / or the, in particular provided by a spring element, elastic support at a sudden pressure peak can be avoided.

The sealing unit is preferably designed to be pressable in the axial direction on the sealing partner. The particular substantially annular sealing unit may be arranged substantially coaxially to the axis of rotation. Due to the relative movability of the sealing unit to the sealing partner in the axial direction, the sealing unit can easily adjust occurring wear by the sealing unit to the extent of wear further axially displaced to the sealing partner and / or deformed. Since the sealing unit is displaced by the pressure of the pressure fluid, in particular compressed air, the pressure of the pressure fluid itself can axially displace the sealing unit for adjusting the wear-related axial misalignment. A leakage of the pressurized fluid caused by wear effects of the sealing unit at a sealing contact point between the sealing unit and the sealing partner can thereby be avoided. Since the substantially annular sealing unit presses against the sealing partner on its axial side, in the case of abrasive wear, only an axial offset of the sealing unit is sufficient to readjust the wear. In particular, it avoids thereby widening an annular component for wear adjustment. This makes it possible to provide particularly wear-resistant materials at the sealing contact point, which usually have poor elasticity and can hardly be widened. Instead of a lateral surface facing in the radial direction, an end face of the annular sealing unit pointing in the axial direction can be pressed on. In comparison to a sealing unit acting in the radial direction, a lower wear can be achieved thereby.

Particularly preferably, the sealing partner, in particular via a spring element, elastically supported offset in the radial direction to a resulting contact pressure of the seal unit. The sealing partner is thus not centrally in the radial direction, but rather elastically supported on the radially outer or radially inner edge. As a result, the sealing partner can be supported on rolling elements of a rolling bearing of the wheel bearing past the outer ring or on the inner ring of the rolling bearing.

In particular, the sealing partner is elastically supported both in the axial direction and in the radial direction. In particular, in an off-center support of the sealing partner, the elastic support both axial and radial portions of an attacking force and / or a elastically support occurring bending moment. Tilting of the sealing partner relative to the sealing unit under load can be avoided.

The invention further relates to a wheel bearing for supporting a motor vehicle tire of a motor vehicle, in particular lorries, with a, in particular inner, first bearing ring, a, in particular outer, second bearing ring, between the first bearing ring and the second bearing ring arranged rolling elements for relatively rotatable mounting of the first bearing ring to the second bearing ring and a sealing arrangement according to one of claims 1 to 8 for the radial passage of a pressurized fluid, wherein the seal unit with the first bearing ring and the sealing partner is rotatably coupled to the second bearing ring. Due to the flexible in the pressing direction of the sealing unit resilient sealing partner, a sufficient sealing effect can be achieved over a designated pressure range at the lowest possible contact pressure, so that with a low wear a good sealing effect in a rotary feedthrough for a wheel bearing is possible.

The wheel bearing can also be used outside of an application as a wheel bearing for a tire of a motor vehicle for various applications. For many applications, it is sufficient if the inner diameter of one of the rolling bearings of the at least two-row wheel bearing or single-row wheel bearing between 50 mm inclusive and 160 mm including, in particular, the outer diameter of the bearing between 90 mm and including 230 mm. Preferably, the axial width of the rolling bearing is between 81 mm and 116 mm inclusive. The radial extent of the wheel bearing is thus large enough to accommodate the seal assembly and the seal assembly can still manufacture and assemble cost. If a common bearing ring is used for the two bearings, which receives in particular the seal holder of the seal assembly, a corresponding twice as large axial width can be provided for the provided for both bearings bearing ring. For ease of assembly, the bearing ring may have a slightly larger axial dimension, for example, between 165 mm and 250 mm inclusive.

Preferably, a further first bearing ring, a further second bearing ring and between the other first bearing ring and the other second bearing ring arranged further rolling elements are provided for relatively rotatable mounting of the other first bearing ring to another second bearing ring, wherein the seal arrangement between the first bearing ring and the other first bearing ring is axially fixed. The wheel bearing can be designed in two rows, wherein the seal arrangement between the two separate bearings of the double row wheel bearing can be fixed axially with a minimum play of for example 200 microns by axial stops of the bearings. In this case, in particular, the seal holder and the further seal holder can be pressed toward one another, so that a flow of pressurized fluid between the seal holders can be avoided past the pressure chambers of the seal holder. In particular, the rolling bearings are designed as angular contact ball bearings and / or tapered roller bearings. As a result, the bearing rings, which clamp the seal assembly substantially and / or fix axially, are pressed towards each other during operation and automatically clamp the seal assembly substantially free of play and / or axially fix.

Particularly preferably, the sealing partner on the second bearing ring is elastically and / or elastically supported on a non-rotatably connected to the second bearing ring hub, in particular wheel hub for attachment of a motor vehicle tire. As a result, the sealing partner can be supported on rolling elements of a rolling bearing of the wheel bearing past the outer ring or on the inner ring of the rolling bearing. In addition, it is possible to prevent tilting of the sealing partner relative to the sealing unit under load.

• 1: eine schematische Schnittansicht einer Drehdurchführung für ein Radlager,
• 2: eine schematische Schnittansicht einer ersten Ausführungsform eines Radlagers mit der Drehdurchführung aus 1 zu einem ersten Zeitpunkt,
• 3: eine schematische Schnittansicht des Radlagers aus 2 zu einem zweiten Zeitpunkt,
• 4: eine schematische Schnittansicht des Radlagers aus 2 zu einem dritten Zeitpunkt,
• 5: eine schematische Schnittansicht des Radlagers aus 2 zu einem vierten Zeitpunkt und
• 6: eine schematische geschnittene Detailansicht des Radlagers aus 2.

The invention will now be described by way of example with reference to the accompanying drawings with reference to preferred embodiments, wherein the features shown below, both individually and in combination may represent an aspect of the invention. Show it:

• 1 FIG. 2: a schematic sectional view of a rotary feedthrough for a wheel bearing, FIG.
• 2 : A schematic sectional view of a first embodiment of a wheel bearing with the rotary feedthrough from 1 at a first time,
• 3 : A schematic sectional view of the wheel bearing from 2 at a second time,
• 4 : A schematic sectional view of the wheel bearing from 2 at a third time,
• 5 : A schematic sectional view of the wheel bearing from 2 at a fourth time and
• 6 : a schematic sectional detailed view of the wheel bearing 2 ,

In the 1 illustrated rotary feedthrough 10 For example, from a radially inwardly connected pressure source in particular as Compressed air pressure fluid through a wheel bearing 12 of a motor vehicle pass into a radially outer pressure space, which may be a tire tube of a motor vehicle tire to adjust the different for different conditions Randbedingen optimal tire pressure can. The rotary feedthrough 10 has a first ring for this purpose 14 on, having a radially extending inlet 16 over which the pressure provided by the pressure source can be applied. The first ring 14 can in this case by the inner ring of the wheel bearing 12 be educated. The wheel bearing 12 is designed, for example, two rows and can in particular two separate bearings 18 have, which have a common inner ring or separate inner rings. The separate inner rings may each have a recess in particular at their mutually facing axial sides in order to jointly the inlet 16 train. The rotary feedthrough 10 also has one to the first ring 14 relatively rotatable second ring 20 on, which has a radially extending outlet 22 has to direct the pressurized fluid in the pressure space. The second ring 20 can in this case by the outer ring of the wheel bearing 12 be educated. Analogous to the first ring 14 can also be the second ring 20 by separate outer rings of the individual rolling bearings 18 of the multi-row wheel bearing 12 be formed, in particular, the separate outer rings may each have a recess at their mutually facing axial sides to jointly the outlet 22 train. The second ring 14 Can also be separate to the outer rings of the wheel bearing 12 be configured and be formed for example by a hub for the tire.

To the first ring 14 and the second ring 20 as tight and wear-resistant seal against each other, has the rotary feedthrough 10 one in the radial direction between the first ring 14 and the second ring 20 arranged sealing arrangement 24 on. The assembled in the illustrated embodiment of two mirror-inverted separate assemblies seal assembly 24 has in the example left assembly a seal holder 26 on, the inlet side with the first ring 14 rotatably connected. For this purpose, for example, the first ring 14 composite inner rings of separate rolling bearings 18 the seal holder 26 between each trained axial stops 28 jam and fix axially. The seal holder 26 one can go to the first ring 14 opened first sealing groove 30 in which, for example, an unillustrated O-ring can be accommodated to the seal holder 26 opposite the first ring 14 Sufficient to seal. The seal arrangement 24 has a, in particular through the two modules assembled connection channel 32 on, looking at the inlet 16 of the first ring 14 followed. From the connection channel 32 branches in the axial direction of an inlet channel 34 starting in a pressure chamber 36 empties. The pressure chamber 36 is on a axially outwardly facing side of a sealing unit 38 sealed inside the seal holder 26 displaced in the axial direction and / or can be elastically deformed. The seal unit 38 has a, in particular made of an elastomeric material, retaining ring 40 on, at his from the pressure chamber 36 away-facing axial side, in particular elastic, receiving pockets 42 in which in each case a rather wear-resistant inelastic support ring 44 and a rather elastic sealing ring 46 are used. Between the receiving bag 42 and the recorded ring 44 . 46 a compensation groove can be provided. The support ring 44 and the sealing ring 46 are essentially concentric with a rotation axis 48 of the wheel bearing 12 arranged, with the rotary feedthrough 10 and the seal assembly also about this axis of rotation 48 can rotate. By the pressure in the pressure chamber 36 can the retaining ring 40 the sealing unit 38 be pressed axially outwards, so that the support ring 44 and the sealing ring 46 in the axial direction against a sealing partner 50 be pressed, whereby one of the pressure in the pressure chamber 36 dependent sufficient and automatically adapted to changing pressure conditions sealing is achieved. The sealing partner 50 is rotatable with the second ring 20 attached. In addition, the sealing partner points 50 one to the second ring 20 opened second sealing groove 52 on, in which, for example, an unillustrated O-ring may be used to the sealing partner 50 opposite the second ring 20 Sufficient to seal. The seal unit 38 rotates at the speed of the first ring 14 while the sealing partner 50 with the speed of the second ring 20 rotates. For abrasive wear of the support ring 44 and the sealing ring 46 reduces the axial extent of the support ring 44 and the sealing ring 46 , The seal unit 38 However, this wear can compensate automatically by the retaining ring 40 by the pressure in the pressure chamber 36 stronger to the sealing partner 50 shifted and / or elastically deformed.

From the pressure chamber 36 goes an exhaust duct 54 which has a significantly smaller flow cross-section than the inlet channel 34 having. The outlet channel 54 can thereby in the manner of a throttle when filling the pressure space the pressure fluid in the pressure chamber 36 dam and generate a dynamic pressure. The kinetic energy of the pressurized fluid is due to the throttling action of the intake passage 34 in an increase of the static pressure in the pressure chamber 36 converted, where appropriate, the density of the pressurized fluid in the pressure chamber 36 can increase. When the pressurized fluid is the outlet channel 54 that has happened Pressurized fluid from the outlet channel 54 to the outlet 22 and to the pressure room. A part of the pressure fluid can also be in between the sealing partner 50 and the sealing unit 38 trained back pressure gap 56 flow and jam there. As a result, the contact pressure of the sealing unit 38 at the sealing partner 50 be reduced.

The second assembly of the seal assembly, sealing off to the right, may comprise a further seal holder 58 with another sealing unit 60 have, in the illustrated embodiment, a mirror image symmetrical to the first assembly with the seal holder 26 and the sealing unit 38 are designed and work analogously.

If the pressure space is to be filled with a pressure fluid to increase the pressure, first, the pressure fluid through the inlet 16 be supplied from a pressure source, as in 2 shown. Subsequently, the pressurized fluid from the inlet 16 over the connection channel 32 on the inlet channels 34 be distributed and in the respectively connected pressure chamber 36 to enter, as in 3 shown. By the pressure in the pressure chamber 36 become the seal units 38 . 60 against their respective sealing partner 50 pressed. Due to the throttling effect of the outlet channel 54 is due to the dynamic pressure achieved by a correspondingly high pressure in the pressure chamber 36 a, which leads to a good sealing effect between the sealing units 38 . 60 and the respective sealing partner 50 leads. As in 4 Finally, the pressurized fluid can be represented via the outlet channel 54 the pressure chamber 36 leave and over the outlet 22 in the second ring 20 , which may be formed by a hub of the motor vehicle tire, get to the pressure space. As in 5 However, a part of the pressure medium can also be represented by a connection between the respective seal holder 26 . 58 and the second ring 20 formed gap in the counter-pressure gap 56 reach. Because of that with the help of the exhaust duct 54 increased pressure in the pressure chamber 36 is at the sealing contact point between the respective sealing unit 38 . 60 and the associated sealing partner 50 given a sufficient sealing effect to prevent leakage or at least to keep low. Due to the gradual pressure equalization between the pressure source and the pressure space, the pressure in the back pressure gap 56 also gradually increase and the contact pressure of the seal units 38 . 60 at the assigned sealing partner 50 to a still sufficient but less weary extent.

The rolling bearing 18 of the wheel bearing 12 can between the inner ring and the outer ring rolling elements 62 respectively. An ingress of dirt can by a designed, for example, as a cartridge seal sealing body 64 be avoided, which is arranged at the axial outer edge of the rolling bearing between the inner ring and the outer ring.

As in 6 the sealing partner can be represented 50 a spring element 66 have, which is formed in the illustrated embodiment as an elastomeric body. About the resilient support forming a spring element 66 is the sealing partner 50 in the axial direction on the outer ring of the respective rolling bearing 18 and in the radial direction on the second ring formed by a wheel hub 20 elastically supported. Between the on the sealing unit 38 . 60 essentially in the radial direction extending part of the sealing partner 50 and the rolling elements 62 the rolling bearing 18 is formed in the axial direction sufficiently large gap, in which the sealing partner 50 at a correspondingly high pressure in the pressure chamber 36 can spring in without on the rolling elements 62 or one of the rolling elements 62 to strike holding bearing cage. Unnecessary high contact pressure of the sealing unit 38 . 60 to the associated sealing partner 50 can be avoided, so that wear of the seal unit 38 . 60 can be kept low. Too much axial displacement of the seal unit 38 . 60 to the respective rolling bearing 18 to is through one of the seal holder 26 . 58 axially acting limit stop 68 avoided. The limit stop 68 can protrude in the radial direction and one in the seal holder 26 . 58 tapered trained opening pointing to the sealing partner, so that the sealing unit 38 . 60 even at a high pressure in the pressure chamber 36 captive in the seal holder 26 . 58 is restrained.

LIST OF REFERENCE NUMBERS

10

Rotary union

12

Wheel bearings

14

first ring

16

inlet

18

Rolling

20

second ring

22

outlet

24

sealing arrangement

26

seal holder

28

axial stop

30

first sealing groove

32

connecting channel

34

inlet channel

36

pressure chamber

38

sealing unit

40

retaining ring

42

receiving pocket

44

support ring

46

seal

48

axis of rotation

50

sealing partner

52

second sealing groove

54

exhaust port

56

Backpressure gap

58

additional seal holder

60

further sealing unit

62

rolling elements

64

sealing body

66

spring element

68

limiting stop

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102015212641 A1 [0003]

Claims (10)

Sealing arrangement for a wheel bearing (12) of a motor vehicle, in particular a truck, with a sealing partner (50) rotatable about an axis of rotation (48), a sealing unit (38) arranged essentially coaxially with the axis of rotation (48) and rotatable relative to the sealing partner (50) for producing a sealing contact with the sealing partner (50), wherein the sealing unit (38) is designed to be displaceable and / or elastically deformable relative to the sealing partner (50) in order to change a contact pressure force on the sealing partner (50), wherein the sealing partner (50) is elastically supported on a rear side facing away from the sealing unit (38). Seal arrangement according to Claim 1 characterized in that the sealing partner (50) on its rear side, in particular made of an elastomeric material, spring element (66). Seal arrangement according to Claim 2 characterized in that the spring element (66) below a predefined limit spring force has a higher spring constant than above the limit spring force. Seal arrangement according to Claim 2 or 3 characterized in that the spring element (66) at least partially has a progressive spring characteristic. Sealing arrangement according to one of Claims 1 to 4 characterized in that the sealing unit (38) in a seal holder (26) is received relatively movable and / or elastically deformable, wherein the seal holder (26) has a limit stop (68) for limiting a maximum relative mobility and / or elastic deformability of the sealing unit ( 38) relative to the sealing partner. Sealing arrangement according to one of Claims 1 to 5 characterized in that the sealing unit (38) in the axial direction on the sealing partner (50) is designed to be pressed. Seal arrangement according to Claim 6 characterized in that the sealing partner (50), in particular via a spring element (66), in the radial direction to a resulting contact force of the sealing unit (38) is elastically supported offset. Sealing arrangement according to one of Claims 1 to 7 characterized in that the sealing partner (50) is elastically supported both in the axial direction and in the radial direction. Wheel bearing for supporting a motor vehicle tire of a motor vehicle, in particular lorries, with a, in particular inner, first bearing ring, one, in particular outer, second bearing ring, arranged between the first bearing ring and the second bearing ring rolling elements (62) for relatively rotatable mounting of the first bearing ring to the second Bearing ring and a seal assembly (24) according to one of Claims 1 to 8th for radial passage of a pressure fluid, wherein the sealing unit (24) with the first bearing ring and the sealing partner (50) is rotatably coupled to the second bearing ring. Wheel bearing after Claim 9 characterized in that the sealing partner (50) is elastically supported on the second bearing ring elastically and / or on a non-rotatably connected to the second bearing ring hub (20), in particular wheel hub for fastening a motor vehicle tire.

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