WO2014177139A1

WO2014177139A1 - Bearing having a rotary feed-through

Info

Publication number: WO2014177139A1
Application number: PCT/DE2014/200064
Authority: WO
Inventors: Horst Brehm; Sergej Mensch; Eduard Beresch
Original assignee: Schaeffler Technologies Gmbh & Co. Kg
Priority date: 2013-04-30
Filing date: 2014-02-17
Publication date: 2014-11-06
Also published as: DE102013207855B4; DE102013207855A1

Abstract

The invention relates to a bearing (1) comprising a first bearing component (3) and a second bearing component (4), wherein the first bearing component (3) and the second bearing component (4) are rotatable relative to one another about a common axis (5), and wherein a first outer surface (40) of the first bearing component (3) and a second outer surface (41) of the second bearing component (4) form an annular gap (35), and wherein from the first outer surface (40) and from the second outer surface (41) a respective duct (20, 28) leads into the respective bearing component (3, 4), characterised in that a circumferential first ring (44) rests on the first outer surface (40) and in that a circumferential second ring (50) rests on the second outer surface (41), wherein the first ring (44) and the second ring (50) in the annular gap (35), overlapping each other at least partially in the radial direction, form a feed-through channel (56) which is in fluid connection with the ducts (20, 28) in respective bearing components (3, 4) by means of at least one respective feed-through opening (72, 73) in the respective ring (44, 50), and in that means (75) for sealing the feed-through channel (56) with respect to the annular gap (35) are introduced.

Description

Name of the invention

Bearing with rotary union Description

Field of the invention

The invention relates to a bearing having a first bearing component and a second bearing component, wherein the first bearing component and the second bearing component are rotatable relative to each other about a common axis, and wherein a first lateral surface of the first bearing component and a second lateral surface of the second bearing component an annular gap form, and wherein in each case a line leads into the respective bearing component of the first lateral surface and of the second lateral surface. The invention further relates, in particular, to a tire pressure regulating system with such a bearing.

BACKGROUND OF THE INVENTION For motor vehicles, it is often useful to adapt the tire pressure to the respective operating situation or to the load. A lower tire pressure increases the footprint, which in commercial vehicles on soft ground, for example, on unpaved roads or dug surfaces, reduced sinking. Higher tire pressure, on the other hand, minimizes rolling resistance on a hard ground and thus reduces fuel consumption, but too high tire pressure can lead to highly irregular tire wear. Therefore, it is also useful for passenger vehicles to make a situation-dependent adjustment. For such an adaptation to the conditions tire pressure regulating systems are used in motor vehicles, with which via a rotary feedthrough compressed air is transmitted from a compressed air source in the vehicle to the rotatably mounted wheel. In this case, in addition to a supply line for tire compressed air, a control air channel can also be provided. be seen over which a tire valve is opened by pressurization. This serves as security against unwanted loss of air.

WO 2012/031880 A1 discloses a bearing in which the stator is formed by a stub axle on the vehicle side and the rotor is formed by a radially arranged wheel hub which is rotatable about the stator, a rotary leadthrough being mounted between the rotor and the stator. In such a bearing engages a cross-sectionally T-shaped rotor flange, from which a line leading to the tire valve in a stator arranged on the annular groove into which a compressed air line of the vehicle opens, so that forms an annular chamber between the flange and groove. The necessary for the transmission of compressed air the chamber via axially arranged sealing rings which are activated by control air lines by pressurization, pressed axially against the rotor flange to operate the rotary union and thus produce a fluid-tight transition from the vehicle-side compressed air duct into the line to the tire valve.

Due to the control air ducts for activating the sealing rings disadvantageously creates a permanently increased need for control in vehicle operation. In addition, the concealed control air ducts and the associated boreholes increase the production effort considerably.

OBJECT OF THE INVENTION The invention is based on the object of specifying a bearing with rotary feedthrough of the type mentioned at the outset, which has the least possible need for control and, moreover, is easy to produce. Furthermore, according to an easy to control and easy to produce tire pressure control system should be specified.

Summary of the invention The first-mentioned object is for a bearing with a first bearing component and a second bearing component, wherein the first bearing component and the second bearing component are rotatable relative to each other about a common axis, and wherein a first lateral surface of the first bearing component and a second outer surface of the second bearing component form an annular gap, and wherein in each case leads from the first lateral surface and from the second lateral surface a respective line into the respective bearing component, according to the invention solved in that the first lateral surface is a circumferential first ring, and in that the second lateral surface is a circumferential second ring, wherein the first ring and the second ring in the annular gap, at least partially overlapping in the radial direction, form a feedthrough channel, which is fluidly connected to the lines in the respective bearing component by at least one flow opening in the respective ring, and means for Abdic hets of the feedthrough channel are provided against the annular gap.

In a first step, the invention is based on the fact that, in a bearing according to the prior art, the control air ducts basically only serve to activate the seals in the rotary union and are therefore superfluous as soon as the sealing function is also achieved in another way in a rotary union can. Surprisingly, the invention recognizes in a second step that, with a skillful choice of the cross-sectional geometry of the feedthrough channel, means for sealing it can be introduced into the channel itself. In particular, these sealing means can be configured such that the sealing effect improves considerably when pressure is applied to the lead-through channel. Due to the sealing functionality of the feedthrough channel, the control air channels can be saved. In particular, in the operating state of a vehicle-side compressed air line via the passage channel is a substantially fluid-tight connection with a wheel-side line to the tire valve.

In particular, the desired geometry is achieved in that in the annular gap between the rotor and stator on the rotor and on the stator in each case a circumferential Ring is mounted so that, viewed in cross-section, in a first ring, a second ring is inserted. Thus there is the least possible surface to be sealed along the rings. In this case, the termination in the axial direction can optionally be completed with a further, ring-shaped workpiece rotatably connected to the first ring. The first ring is due to the pressure forces acting axially on him conveniently made of a metal, the second ring can be made of a sufficiently hard plastic to reduce weight. In an advantageous embodiment of the invention in the first and / or second lateral surface under the respective seated ring at least partially circumferential collecting channel is introduced, in which opens the or each line of the respective bearing component, wherein connected through the collecting channel, the respective line with the feed channel fluidly is. This connection of the respective collecting channel with the passage channel increases the effective cross-sectional area of the rotary feedthrough, which leads to an increased air transfer at the same air pressure. In addition, slippage of the ring can be permitted by means of a collection channel on a ring, since any flow opening in the ring need not be localized for fluid exchange with the collection channel. Thus, any fasteners such as screws or rivets are saved. Preferably, a ring should be rotatably mounted on a bearing component to avoid tangential frictional forces. If necessary, at the bearing, axially offset from the first feedthrough, a further feedthrough channel may be provided in the annular gap, which may be substantially equal to the first, that is, on the first lateral surface a third circumferential ring is seated, and that on the second lateral surface fourth circumferential ring is seated, wherein the third ring and the fourth ring in the annular gap, at least partially overlapping in the radial direction, form a further passage channel, and wherein in the third and fourth ring in each case a flow opening is attached, from which in each case one Line leads into the respective bearing component, and that means are provided for sealing the second passageway in the annular gap. This may be necessary if compressed air is to be conducted to a wheel-side tire valve via a rotary feedthrough on the bearing of a vehicle-side compressed air supply line, and also a control channel is provided for activating the valve, the compressed air of which also has to be supplied from the vehicle-side source via the bearing ,

Conveniently, there is a circumferential collar on the first ring, wherein the collar axially delimits the feed-through channel against the annular gap in one direction. In the axially other direction of the feedthrough channel is limited by a separate annular workpiece which is rotatably connected to the first bearing member. In particular, the first ring has a substantially L-shaped cross-section, so that it rests with a thigh surface on the first lateral surface and the other leg surface forms the encircling collar. Thus, the axial delimitation of the feed-through channel in the other direction can take place via end faces of a further annular workpiece, which still performs other functions on the bearing, which generally leads to a material and thus weight and also cost reduction.

In the case of an axial arrangement of several feedthrough channels in a bearing, such an end face may be formed by the peripheral collar of another ring, so that the circumferential collar of the first ring axially delimits the first feedthrough channel against the second feedthrough channel. In other words, therefore, a collar of a ring forms an axial boundary of two adjacent feedthrough channels. In particular, the second feedthrough channel is bounded axially in the other direction by a circumferential collar on the third ring. This sharing of individual parts in several axially arranged feedthrough channels requires a considerably simplified installation of several rotary feedthroughs. In an independent inventive embodiment, a sealing ring is provided as means for sealing the passage channel, which in the region of the radial overlap of the first and second circumferential ring is such that it with two of its circumferential surfaces sealingly against the first and at the same time to the second ring is pressed when the passage channel is pressurized. Thus, a self-regulation of the sealing of the feedthrough channel is achieved in a particularly simple manner. In particular, this can be achieved by a substantially right-angled triangular cross-section of the sealing ring, wherein the hypotenuse corresponding sealing ring surface faces the feed channel and the sealing surfaces corresponding to the catheter abut the first and second ring. As a result, when pressure is applied, the sealing ring is pressed into the joint between the first and the second ring. Each duct can also be sealed by axially offset pairs of sealing rings of the type mentioned. The sealing ring can be made of an elastomer, and optionally lie in a guide groove of the second ring, or be made as a compact component with this and thus form a kind of sealing lip at its edge.

In an expedient variant, the bearing is designed as a roller bearing, which comprises an inner ring, an outer ring and arranged therebetween rolling elements, for example tapered rollers. Thus, a rotary feedthrough on the bearing can also be used for high speeds.

In a particularly advantageous embodiment of the rolling bearing in this case the first bearing member is joined to the inner ring rotation, so that an end face of the inner ring axially bounds the feed channel in one direction. It is thus utilized an already existing part of the camp for one-sided limitation of the feed-through channel, which allows a particularly simple and compact design. The feedthrough channel is then bounded in the other direction by the overlap of the first ring with the second ring. The- The design also has the advantage that you do not have to replace any components on the vehicle side, if no rotary feedthrough is to be used on the warehouse. Instead of the first bearing component, a solid or hollow-walled spacer ring can be inserted in a rotationally fixed manner to the inner ring.

Another preferred possibility is that the first bearing component and the inner ring are made in one piece. On this compact bearing component then in addition to the first ring in particular still sits on a clamping ring which limits the feedthrough channel axially in the direction of the rolling elements. The selection between non-rotatable joining or one-piece production of the first bearing component with the inner ring may depend on the available installation space, the maximum speed range and other operating and design parameters and can thus be optimized for these. The second object is achieved by a tire pressure control system in which a wheel is rotatably mounted on a vehicle via a bearing with rotary feedthrough of the type described above, wherein the wheel side leads a line from the camp to a tire valve, and wherein the vehicle side, a line from the camp a compressed air source leads. By means of a rotary feedthrough on the bearing, compressed air can be used to transmit compressed air to the tire valve, which can optionally be activated by a control air duct. For such a control air duct, air is supplied from the vehicle to another air source from a second rotary feedthrough on the bearing up to an actuator on the valve. As a compressed air source, for example, a vehicle-side compressor can be used. The advantages stated for the bearing and its developments can be transferred analogously to the tire pressure control system.

Brief description of the drawings

Embodiments of the invention will be explained in more detail with reference to a drawing. In each case show in longitudinal section: 1 shows a bearing with rotary feedthrough according to a first variant, configured as a tire pressure control system of a motor vehicle, wherein an inner ring of a rolling bearing and a first bearing component are made in one piece,

2 shows a section of the tire pressure control system according to FIG. 1 in an enlarged view, FIG. 3 shows a detailed view of the rotary unions on the bearing according to FIG. 2,

4 shows a detail of a rotary feedthrough of a bearing according to a second variant in an enlarged view, wherein an inner ring of a rolling bearing and a first bearing component are joined together in a rotationally fixed manner,

5 shows a bearing of a motor vehicle with a spacer ring for bridging the rotary feedthrough. Detailed description of the drawings

In Fig. 1, a bearing 1 is shown with a tire pressure control system 2. The wheel-side first bearing component 3 is rotatably mounted on tapered rollers 10 of a rolling bearing 12 in the vehicle-side second bearing component 4 with respect to a common axis 5, which ends at a wheel hub 6 with wheel bolt 7. The tapered rollers 10 are incorporated in the outer ring 14 of the rolling bearing 12, wherein in this embodiment, the inner ring 16 of the rolling bearing 12 is made in one piece with the first bearing component 3. From the first bearing component 3, a line 20 leads to a valve 22 on a tire 26 mounted on a rim 24. A line 28 leads from the second bearing component 4 to a compressed-air source 30 on the vehicle 32. Rotary feedthroughs 42 and 43 are provided in the annular gap 35 between the first lateral surface 40 of the bearing component 3 and the second lateral surface 41 of the bearing component 4, the components of which are described in detail in FIG. On the wheel-lateral surface 40 sits a cross-sectionally L-shaped first ring 44 with its axial leg surface 45, so that its radial leg surface 46 forms a circumferential collar in the annular gap 35. In the lateral surface 40, a first collecting channel 48 is introduced under the first ring 44, from which the line 20 leads away from the wheel side to the tire valve 22, which is not shown in the figure. On the vehicle-side lateral surface 41 sits a second ring 50. In the second lateral surface 41, below the second ring 50, there is a second collecting channel 52, from which the line 28 on the vehicle side leads to the compressed-air source 30, not shown in the figure. The second ring 50 forms, with the first ring 44 and a clamping ring 54 circulating on the first bearing component 3 in the vicinity of the tapered rollers 10, a first feedthrough channel 56, the mode of operation of which is explained in FIG.

Axially offset from the rotary leadthrough 42, another rotary leadthrough 43 is provided in the annular gap 35, which is essentially identical to the first rotary leadthrough 42. On the first lateral surface 40 sits a cross-sectionally L-shaped third ring 60, under which in the lateral surface 40, a third collecting channel 62 is introduced, leading away from the wheel side, a line not shown in the drawing. This line is offset in the circumferential direction against the line 20 of the first rotary feedthrough 42. On the vehicle-side lateral surface 41 sits a fourth ring 64, under which in the second lateral surface 41, a fourth collecting duct 66 is located, leading away from the vehicle side to a line not shown in the drawing. This line is offset in the circumferential direction against the line 28 of the first rotary feedthrough 42. The fourth ring 64 forms with the third ring 60 and the radial leg surface 46 of the first ring 44, a second passage channel 68. To seal the annular gap 35 against the ingress of dirt is located at its axially wheel-side end Cassette seal 70. The rings 44 and 60 or 50 and 64 of the two feedthrough channels 56, 68 are each identical in construction.

In Fig. 3, the rotary feedthrough 42 is shown in detail. In the first ring 44 and the second ring 50 are flow openings 72, 73 for the fluidic connection of the collecting channels 48, 52 with the passage channel 56. On the second ring 50 guide grooves 74 are radially mounted in the passage channel, in which sealing rings 75 are mounted. The cross-section of these sealing rings 75 is, except for flattening at the edges, substantially rectangular-triangular, wherein the hypotenuse corresponding surface 76 faces freely the feedthrough channel 56, and the corresponding surfaces of the cathodes 77 and 78 on the second ring 50th or on the axial boundary surfaces of the feedthrough channel 56, which are formed by the radial leg surface 46 of the first ring and the circumferential clamping ring 54, sit. Upon pressurization of the passage channel 56 through the conduit 28 via flow openings 73, the sealing rings 75 are now pressed by pressure on the Hypotenuseflächen 76 with the Kathetenflächen 78 and 77 fixed to the axial boundary surfaces 54 and 46 and the second ring 50, and thus is about the flow opening 72 produces a fluid-tight connection from the vehicle-side compressed-air line 28 to the wheel-side compressed-air line 20.

In the second passage channel 68, which is formed by the radial leg surface 46 of the first ring 44, as well as the third ring 60 and the fourth ring 64 and fluidly connected via flow openings 80, 81 with the collecting channels 62, 66, there are sealing rings 82 which in this illustration the sealing rings 75 are identical in construction and function.

4, a further embodiment of the bearing 1 is shown. In this variant, the inner ring 84 of the rolling bearing 12 is non-rotatably joined with the first bearing component 3. The end face 86 of the inner ring 84, together with the radial leg surface 46 of the first ring forms the axial boundary of the first feedthrough channel 56. The sealing ring 88 seals the feedthrough channel 56 now on the end face 86 of the inner ring 84. Both shown feedthrough channels 56 and 68 are otherwise completely identical to the feedthrough channels 56 and 68 shown in FIG. 3. In FIG. 4, a line 90 which leads away from the third collecting channel 62 to a non-illustrated actuator on the tire valve 22, as well as a Line 92, which leads vehicle side of the fourth collection channel 66 to a control air source, not shown, shown. Both lines 90, 92 are each offset in the direction of rotation to the lines 20 and 28 shown in FIG. 2.

In Fig. 5, a bearing 1 is shown, in which the first bearing member 3, which is non-rotatably joined with the inner ring 84 of the rolling bearing 12, is formed by a simple spacer ring 94, so that in the annular gap 35 no lead-through channels are provided. Only a cassette seal 70 is mounted in the annular gap 35 to protect the rolling bearing 12 from dirt. The bearing 1 can thus also be used without changes on the vehicle side and only through modular replacement of annular component groups on the wheel, if a rotary feedthrough is not required and, for cost reasons, is also undesirable.

LIST OF REFERENCE NUMBERS

1 bearing

2 tire pressure control system

3 first bearing component

4 second bearing component

5 axis

6 wheel hub

7 wheel bolts

10 tapered rollers

12 rolling bearings

14 outer ring

16 inner ring (made in one piece with the first bearing component)

20 compressed air line to the tire

22 tire valve

24 rim

26 tires

28 Compressed air line in the vehicle

30 compressed air source

32 vehicle

35 annular gap

40 first lateral surface

41 second lateral surface

42 first rotary feedthrough

43 second rotary feedthrough

44 first ring

45 axial leg surface of the first ring

46 radial leg surface of the first ring

48 first collection channel

50 second ring

52 second collection channel

54 clamping ring 56 first feedthrough channel

60 third ring

62 third collection channel

64 fourth ring

66 fourth collection channel

68 second passage channel

70 cassette seal

72 flow opening in the first ring

73 Flow opening in the second ring

74 guide troughs

75 sealing rings in the first feedthrough channel

76 Hypotenuse surface of the sealing ring

77 Catheter surface of the sealing ring to the second ring

78 Catheter surface of the sealing ring to the first ring

80 flow opening in the third ring

81 Flow opening in the fourth ring

82 sealing rings in the second feedthrough channel

84 inner ring (non-rotatably joined with first bearing component)

86 end face of the inner ring

88 sealing ring

90 Line to the third collection channel

92 Line to the fourth collection channel

94 spacer ring

Claims

claims

Bearing (1) with a first bearing component (3) and a second bearing component (4), wherein the first bearing component (3) and the second bearing component (4) are rotatable relative to each other about a common axis (5), and wherein a first lateral surface (40) of the first bearing component (3) and a second lateral surface (41) of the second bearing component (4) form an annular gap (35), and wherein from the first lateral surface (40) and from the second lateral surface (41) in each case a line ( 20, 28) into the respective bearing component (3, 4), characterized in that the first lateral surface (40) is seated in a circumferential first ring (44), and in that the second lateral surface (41) is seated on a peripheral second ring (50), wherein the first ring (44) and the second ring (50) in the annular gap (35), at least partially overlapping in the radial direction, form a feed-through channel (56) which is connected to the lines (20, 28) in the respective bearing component (3, 4) in each case by at least one flow opening (7 2, 73) is fluidically connected in the respective ring (44, 50), and in that means (75) are provided for sealing the feedthrough channel (56) against the annular gap (35).

Bearing (1) according to claim 1, characterized in that in the first (40) and / or second lateral surface (41) under the respective seated ring (44,50) at least partially circumferential collecting channel (48,52) is introduced, in the or each line (20,28) of the respective bearing component (3,4) opens, wherein through the collecting channel (48,52) the respective line (20,28) with the passage channel (56) is fluidically connected.

Bearing (1) according to one of the preceding claims, characterized in that on the first lateral surface (40) a third circumferential ring (60) is seated, and that on the second lateral surface (41) a fourth circumferential ring (64) is seated, wherein the third ring (60) and the fourth Ring (64) in the annular gap (35), at least partially overlapping in the radial direction, form a further feed-through channel (68), which is axially offset from the first feed-through channel (56), and wherein in the third ring (60) and in the fourth ring ( 64) in each case a flow opening (80,81) is mounted, from which in each case a line (90,92) into the respective bearing member (3,4) leads, and that means (88) for sealing the second passage channel (68) in the annular gap (35) are provided. 4. bearing (1) according to any one of the preceding claims, characterized in that on the first ring (44) is a circumferential collar (46), wherein the federal limits the passage channel (56) against the annular gap (35) axially in one direction and wherein the feedthrough channel (56) is bounded axially in the other direction by a separate ring-shaped workpiece (54, 84) which is non-rotatably connected to the first bearing component (3), and in particular the first ring (44). has a substantially L-shaped cross section, so that it is seated with a leg surface (45) on the first lateral surface (40) and the other leg surface (46) forms the circumferential collar.

5. Bearing (1) according to claim 3 and claim 4, characterized in that the circumferential collar (46) of the first ring (44) delimits the first feedthrough channel (56) axially against the second feedthrough channel (68).

6. Bearing (1) according to one of the preceding claims, characterized in that as means for sealing the passage channel, a sealing ring (75) is provided, which in the region of the radial overlap lapps the first circumferential ring (44) and the second circumferential

Rings (50) is applied, in particular, that the sealing ring has a substantially triangular cross-section. Bearing (1) according to one of the preceding claims, characterized in that the bearing is designed as a rolling bearing (12) comprising an inner ring (16,84) and an outer ring (14), and between the inner ring (16,84) and the Outer ring (14) arranged rolling elements (10).

Bearing (1) according to claim 7, characterized in that the first bearing component (3) with the inner ring (84) is non-rotatably joined, in particular, that an end face (86) of the inner ring (84) the feedthrough channel (56) axially in one direction limited.

Bearing (1) according to claim 7, characterized in that the first bearing component (3) and the inner ring (16) are made in one piece.

Tire pressure control system (2), characterized in that a wheel is rotatably mounted on a vehicle (32) via a bearing (1) according to one of claims 1 to 9, wherein the wheel side a line (20) from the bearing (1) to a tire valve ( 22), and wherein on the vehicle side, a line (28) from the bearing (1) leads to a compressed air source (30).