Plain bearing or rolling bearing equipped with a sealing device having a sealing seat close to the rotation axis

Abstract

A bearing (10) includes an inner ring (36), an outer ring (20), and a seal arrangement (66). The seal arrangement (66) includes at least an outer structure (76) secured to the outer ring (20) and an inner structure (78) secured to the inner ring (36). The inner structure (78) includes a shrink fit portion (88) and at least one seal seat (90), the shrink fit portion being shrink fit to a shrink fit bearing surface (72) of the inner ring (36). The outer structure (76) includes at least one seal lip (86) in sliding contact against the seal seat (90). The seal seat (90) is axially located at a distance from a second axial end wall (74) of the inner ring (36) and is closer to the rotational axis (XX) than the shrink fit bearing surface (72).

Description

Technical Field

[0001] This invention relates to a sliding bearing or a rolling bearing, and specifically, but not exclusively, to a rolling bearing constituting a rolling bearing for a vehicle wheel, preferably a rolling bearing for a drive wheel and a steering wheel. Background Technology

[0002] The electric or hybrid drivetrain systems of certain motor vehicles have reduced the space available for the transmission bowl used to position the drive wheels, leading to the development of components of the type described in the currently unpublished French application FR2000720, in which at least a portion of the wheel's rotational guidance overlaps with the transmission bowl. Such components require wheel bearings with diameters larger than those commonly found in the market. To ensure the sealing of such bearings, a seal is required. For this purpose, a cassette seal, housed directly radially between the inner and outer rings, can be naturally considered. However, such a large-diameter seal presents problems that are difficult to resolve without increasing functional costs. Specifically, friction arises between the sealing lip and the seat, and this friction increases with the diameter, negatively impacting drag torque and operating temperature. Furthermore, large-diameter joints require additional assembly precision and reduced manufacturing tolerances. Finally, inserting the cassette seal into the wheel bearing requires two cylindrical seats facing each other on the outer and inner rings.

[0003] Document US 9,377,055 B2 illustrates a wheel bearing equipped with a sealing device consisting of a conventional cassette seal protected by a chicane seal. The sealing device includes an outer structure secured to the outer ring of the bearing and positioned opposite an inner structure secured to the inner ring of the bearing. These two structures do not contact each other. Again, inserting the cassette seal into the wheel bearing requires two cylindrical support surfaces facing each other on the outer and inner rings.

[0004] Document JP2008138766 describes a wheel bearing equipped with a sealing device comprising an external structure secured to an outer ring of the bearing and an internal structure secured to an inner ring of the bearing. The external and internal structures together define a sealing volume. The internal structure includes a shrink-fit portion that shrinks onto a shrink-fit support surface of the inner ring and at least one sealing seat. The external structure includes at least one sealing lip that slides against the sealing seat to seal the sealing volume. The sealing seat is planar and extends in the direction of the rotation axis to cover a portion of the axial end face of the inner ring. In this arrangement, the seal and sealing seat are directly exposed to contaminants. The sealing seat, rotating with the inner ring, centrifuges the contaminants, causing them to be ejected in the direction of the seal, which is disadvantageous.

[0005] Document WO 2008 / 102 579 A1 describes a wheel bearing equipped with a sealing device comprising an external structure secured to the outer ring of the bearing and an internal structure secured to the inner ring of the bearing, the external and internal structures together defining a sealing volume leading to the internal volume of the bearing. The internal structure includes a shrink-fit portion shrink-fitted to a shrink-fit support surface of the inner ring and at least one sealing seat. The external structure includes at least one sealing lip that slides against the sealing seat to seal the sealing volume. The sealing seat includes a cylindrical member that rotates radially outward and covers the shrink-fit portion; and a planar portion that extends from the cylindrical member in a direction opposite to the axis of rotation. The resulting structure comprises numerous parts and complex components. Furthermore, because the sealing seat is located radially outside the shrink-fit support surface of the internal structure, it is not suitable for large-diameter wheel bearings. Summary of the Invention

[0006] The purpose of this invention is to remedy the shortcomings of the prior art and to provide a sliding bearing or rolling bearing that balances large pitch diameter and satisfactory sealing function from the perspective of technical performance and financial cost.

[0007] Therefore, according to a first aspect of the invention, a sliding bearing or rolling bearing is provided, comprising at least one inner ring and at least one outer ring, the inner ring and the outer ring being rotatable relative to each other about a rotation axis of the bearing, the inner ring having a guide seat ring, the outer ring having at least one guide seat ring positioned opposite the guide seat ring of the inner ring and defining the internal volume of the bearing with respect to the guide seat ring of the inner ring, the inner ring having an axial end face rotatable in a reference axial direction parallel to the rotation axis, the axial end face being axially located at a distance from the guide seat ring of the inner ring along the reference direction, the inner ring having an axial end face axially located between the axial end face of the inner ring and the guide seat ring. The bearing includes a shrink-fit support surface between the rings, and a sealing device comprising at least an external structure secured to the outer ring and an internal structure secured to the inner ring. The external and internal structures together define a sealing volume leading to an internal volume of the bearing. The internal structure includes a shrink-fit portion on the shrink-fit support surface of the inner ring and at least one sealing seat. The external structure includes at least one sealing lip in sliding contact with the sealing seat. The sealing seat and the sealing lip sealing the sealing volume are characterized in that the sealing seat is axially located at a distance from the end wall of the inner ring along a reference axial direction and is closer to the axis of rotation than the shrink-fit support surface.

[0008] According to the invention, the seal seat is radially opposed to the axis of rotation of the bearing. The internal structure further includes a connecting portion and a deflector plate, the connecting portion projecting axially relative to the seal seat in a reference direction, and the deflector plate projecting radially from the mating portion in a radial direction opposed to the axis of rotation. The deflector plate and the external structure form a blocking bend channel leading into the sealing volume, the blocking bend channel having an inlet further away from the axis of rotation than the seal seat, the seal seat and sealing lip being positioned within the sealing volume and between the blocking bend channel and the internal volume of the bearing. The geometry of the blocking bend channel facilitates the centrifugal removal of contaminants penetrating it.

[0009] By placing the seal seat outside the inner ring, the diameter and circumference of the seal seat can be reduced, as well as the frictional torque between the sealing lip and the seal seat, which is particularly advantageous for high pitch diameter bearings.

[0010] Preferably, the bottom of the sealing seat is closer to the axis of rotation than the bottom of the guide ring of the inner ring.

[0011] According to one embodiment, the cylindrical shrinkage assembly support surface of the inner ring is radially away from the axis of rotation of the bearing.

[0012] According to one embodiment, the internal structure includes a frame forming the shrink-fit portion and the sealing seat.

[0013] Preferably, the deflection plate is attached to the frame by fastening, shrink fitting, bonding, fastening elements, or any other means.

[0014] According to one embodiment, the internal structure includes a static sealing portion that supports and abuts a static seal, which is intended to be positioned between the internal structure and a component secured to the inner ring, specifically a drive cup or a sleeve for protecting the drive cup. The static seal allows for protection of the connection between the inner ring and the component mounted thereon.

[0015] According to one embodiment, the internal structure includes an encoder. The encoder enables the encoding of information read by a sensor (particularly position information), which is preferably stationary relative to the external structure.

[0016] According to one embodiment, the guide ring of the outer ring is a raceway, the guide ring of the inner ring is a raceway, and the bearing is a rolling bearing comprising at least one row of rolling elements capable of rolling on both the raceways of the outer and inner rings to allow relative rotational movement between the inner and outer rings about an axis of rotation. In this context, the invention allows the pitch diameter of the rolling bearing to be increased without negatively affecting its resistance torque. Preferably, the seal is closer to the axis of rotation than the pitch circle defined by the row of rolling elements. By reducing the circumference of the seal in this way, the frictional torque of the bearing is reduced.

[0017] According to another aspect of the present invention, the present invention relates to a vehicle wheel support device, characterized in that the vehicle wheel support device includes a bearing according to any one of the preceding claims, the inner ring being a rotating ring, preferably a wheel hub or a ring secured to a wheel hub, and the outer ring being a fixing ring having a joint for attachment to a wheel support (particularly a wheel pivot). Attached Figure Description

[0018] Other features and advantages of the invention will become clear from the following description, which is illustrated in the accompanying drawings:

[0019] Figure 1 : An axial cross-sectional view of a wheel support assembly of a wheel bearing according to a first embodiment of the present invention;

[0020] Figure 2 : Figure 1 Detailed views of certain components of the wheel bearing;

[0021] Figure 3 Detailed views of certain components of a wheel bearing according to a second embodiment of the present invention;

[0022] Figure 4 Detailed views of certain components of a wheel bearing according to a third embodiment of the present invention;

[0023] Figure 5 : Detailed views of certain components of a wheel bearing according to a fourth embodiment of the present invention.

[0024] For clarity, in all the accompanying drawings, the same or similar elements are identified by the same reference numerals. Detailed Implementation

[0025] Figure 1 A motor vehicle drive wheel assembly 10 is shown, comprising: a fixed sub-assembly 12 intended to be secured to a suspension component of a motor vehicle (not shown) and defining a rotation axis XX; a rotating sub-assembly 14 rotatable within the fixed sub-assembly 12 about the rotation axis XX; and a first rolling element 16 and a second rolling element 18 guiding the rotating sub-assembly 14 and the fixed sub-assembly 12.

[0026] The fixing subassembly 12 is here constituted by a one-piece solid metal outer ring 20, on which, in this embodiment, two coaxial first outer raceways 22 and second outer raceways 24 are formed. The first outer raceway 22 and the second outer raceway 24 define a rotation axis XX. One of these outer raceways 22 is intended to be positioned on the outer side of the vehicle, and the other outer raceway 24 is intended to be positioned on the inner side of the vehicle, i.e., closer to the central longitudinal vertical plane of the vehicle. The outer ring further includes at least one radially outwardly extending attachment clamp 26, in which an engagement portion 28 is formed for attaching the attachment clamp 26 to the wheel support 30 via an attachment element 32, in this case, a strut pivot.

[0027] The rotating subassembly 14 includes a wheel hub 34, an inner ring 36 on the inside of the vehicle, and a drive cup 38, wherein the wheel hub 34 forms the inner ring on the outside of the vehicle.

[0028] The wheel hub 34 is a solid, one-piece metal component that includes a flange 40 for attaching the drive wheel rim and the brake disc. The flange 40 has a flat surface 42 supporting the brake disc or wheel rim and is provided with an attachment hole 44, thereby allowing the insertion of attachment elements for the rim and / or brake disc. The wheel hub 34 has a first inner raceway 46 facing the first outer raceway 22.

[0029] The transmission cup 38 is a solid, one-piece metal component. In this embodiment, the transmission cup 38 has a solid protrusion 50 and a flared central portion 52 defining a cavity 54, thus acting as a constant velocity joint. The protrusion 50 of the transmission cup 38 is splinedly connected to the splined tubular cavity 56 of the wheel hub 34 and is freely mounted, fitted, or retracted within the splined tubular cavity 56 of the wheel hub 34, thereby forming a spline contact interface. Furthermore, Figure 1The method for attaching the drive cup 38 and the wheel hub 34 is shown, implemented as a nut 58, which is screwed onto the threaded end of the protrusion 50 and supports against the shoulder of the wheel hub 34. The inner ring 36 on the inner side of the vehicle retracts onto the cylindrical shrink-fit surface 60 of the wheel hub 34 and is clamped between the wheel hub 34 and the drive cup 38 in the axial direction.

[0030] The second inner raceway 62 is formed on the inner ring 36, opposite to the outer raceway 24 on the inner side of the vehicle. On one hand, the first rolling element 16 and the second rolling element 18 are formed on the first outer raceway 22 and the first inner raceway 46 on the outer side of the vehicle, forming a first row of first rolling elements 16. On the other hand, the first rolling element 16 and the second rolling element 18 are formed on the second row of second rolling elements 18 on the outer raceway 24 and the inner raceway 62 on the inner side of the vehicle.

[0031] The two rows of first rolling elements 16, second rolling elements 18, first outer raceway 22, second outer raceway 24, first inner raceway 46, and second inner raceway 62 are protected by two sealing devices: a sealing device 64 located on the outside of the vehicle and a sealing device 66 located on the inside of the vehicle and positioned between the outer ring 20 and the inner ring 36.

[0032] The components of the wheel bearing 10 described so far are general and can be presented in many variations. Specifically, a first inner raceway 46 may be formed on the bearing ring attached to the wheel hub 34. The inner ring 36 on the inner side of the vehicle can be secured to the wheel hub 34 by a retaining ring and, if necessary, does not contact the drive cup 38. The drive cup 38 can be attached to the wheel hub 34 in any manner. The bearing may consist of only one row of first rolling elements 16, which can be balls or rollers.

[0033] Now we will take a closer look at the sealing device 66 located on the inside of the vehicle (in... Figure 2 (As shown in detail below), the sealing device seals the outer ring 20 and the inner ring 36, and more specifically protects the volume V located between the second outer raceway 24 of the outer ring 20 and the second inner raceway 62 of the inner ring 36. In this region, the outer ring 20 has a shrinkage mounting surface 68 and a first axial end wall 70, which is cylindrical and faces the axis of rotation XX. The first axial end wall 70 defines a reference plane PE of the outer ring 20, which is perpendicular to the axis of rotation XX and tangent to the first axial end wall 70. The shrinkage mounting surface 68 extends axially and circumferentially in the region of the outer ring 20 between the second outer raceway 24 and the first axial end wall 70 on the vehicle side. The shrinkage mounting surface 68 on the outer ring is farther from the axis of rotation XX than the pitch circle C of a row of second rolling elements 18, and in this embodiment, farther from the axis of rotation XX than the raceway bottom FE of the second outer raceway 24 of the outer ring 20.

[0034] The inner ring 36 also has a shrink-fit support surface 72 and a second axial end wall 74, the shrink-fit support surface 72 being cylindrical in this case and radially outward, the second axial end wall 74 defining a reference plane PI of the inner ring 36, which is perpendicular to the axis of rotation XX and tangent to the second axial end wall 74. The shrink-fit support surface 72 extends axially and circumferentially in the region between the second inner raceway 62 on the inner side of the inner ring and the second axial end wall 74. The second axial end wall 74 of the inner ring and the first axial end wall 70 of the outer ring rotate in a common axial reference direction D parallel to the axis of rotation XX, which will be the axial reference direction for the remainder of the illustration. In this embodiment, it can be noted that the reference plane PI of the inner ring 36 is located at a certain distance from the reference plane PE of the outer ring 20 and is offset in the axial reference direction D, such that the inner ring 36 protrudes from the outer ring 20 in the axial reference direction D and passes through the reference plane PE of the outer ring 20. More specifically, at least a portion of the shrink-fit support surface 72 of the inner ring 36 is located on the side of the reference plane PE of the outer ring 20 opposite to the shrink-fit surface 68 of the outer ring 20.

[0035] The sealing device 66 includes an external structure 76 integral with the outer ring 20 and an internal structure 78 integral with the inner ring 36.

[0036] The external structure 76 includes a shrink-fit portion 80 that tapers to a shrink-fit surface 68 on the outer ring 20, a functional portion forming a radially outwardly opening groove 82, a blocking corner wall 84, and, in this embodiment, two sealing lips 86. The groove 82 has a bottom 822 and sidewalls 824, the sidewalls 824 being axially located on either side of the bottom and further away from the axis of rotation than the bottom. In this embodiment, the external structure 76 includes a rigid frame 762, for example made of sheet metal or plastic, and an overmolding member 764. The frame 762 forms the shrink-fit portion 80 and the groove 82, while the overmolding member 764 forms the blocking corner wall 84 and the sealing lips 86.

[0037] The internal structure 78 includes a shrink-fit portion 88 that shrinks into the shrink-fit support surface 72 of the inner ring 36, and a functional portion forming a sealing seat 90 and a blocking bend wall 92, which is positioned opposite a blocking bend wall 84 of the outer structure 76 to define a blocking bend channel S between the internal structure 78 and the outer structure 76. A sealing lip 86 is elastically deformable and supported on the sealing seat 90, which in this embodiment is cylindrical. The internal structure 78 and the outer structure 76 together define a sealing volume L for the sealing seat 90 and the sealing lip 86, wherein the blocking bend channel S is open and communicates with an internal volume V defined by the second outer raceway 24 of the outer ring 20 and the second inner raceway 62 of the inner ring 36.

[0038] The functional portions of the shrink-fit assembly 88 and the internal structure 78 are located on either side of the reference plane PI of the inner ring 36. This allows the seal seat 90 to be positioned closer to the axis of rotation XX than the shrink-fit assembly 88. This arrangement is designed to minimize the diameter of the seal seat 90, thereby minimizing the frictional torque between the sealing lip 86 and the seal seat 90, and reducing the heat generated by this friction.

[0039] The blocking bend channel S has an inlet E defined by the inlet portion of the blocking bend wall 84 of the outer structure 76 and the inlet portion of the blocking bend wall 92 of the inner structure 78. The inlet E of the blocking bend channel S and the contraction assembly portion 80 of the outer structure 76 are axially located on opposite sides of the groove 82. The blocking bend channel S and the groove 82 are located on the same side of the reference plane PE of the outer ring 20, opposite to the side of the reference plane PE where the contraction assembly portion 80 of the outer structure 76 is located. The inlet of the blocking bend channel is further away from the rotation axis XX than the sealing seat 90.

[0040] The blocking bend wall 84 of the outer structure 76 is formed by a first annular rib 94 extending axially toward the blocking bend wall 92 of the inner structure 78. Similarly, the blocking bend wall 92 of the inner structure 78 is formed by a plurality of second annular ribs 96 extending axially toward the blocking bend wall 84 of the outer structure 76 and interposed in the gaps between the first annular ribs 94 of the outer structure 76. The first annular ribs 94 of the outer structure 76 form one or more additional grooves 98 located inside the blocking bend channel S. At the second annular ribs 96 of the inner structure 78, the blocking bend wall 92 includes a truncated conical facet 922 rotating toward the axis of rotation and a truncated conical wall 924 rotating radially outward.

[0041] The inlet E of the blocking bend channel S is annular and faces an axial direction opposite to the axial reference direction D, toward the outer ring 20. Inlet E is further away from the axis of rotation XX than the bottom 822 of the groove 82. In this case, inlet E is preferably further away from the axis of rotation XX than the pitch circle C defined by a row of second rolling elements 18.

[0042] As shown in the figure, the entrance portion of the blocking bend wall 92 of the internal structure 78 is preferably truncated conical in shape so as to converge toward a vertex farther away from the outer reference plane PE than the entrance E. Similarly, as shown in the figure, the entrance portion of the blocking bend wall 84 of the external structure 76 is preferably truncated conical in shape so as to converge toward a vertex farther away from the outer reference plane PE than the entrance E.

[0043] In this embodiment, it can be seen that the groove 82 at least partially overlaps axially with the shrinkage assembly support surface 72 of the inner ring 36 and the shrinkage assembly portion 88 of the internal structure 78. The blocking corner wall 84 of the outer structure 76 is located entirely on one side of the reference plane PI of the inner ring 36 and entirely on one side of the groove 82, such that the groove 82 is axially located between the shrinkage assembly portion 80 of the outer structure 76 and the blocking corner wall 84 of the outer structure 76.

[0044] Optionally, the functional portion of the internal structure 78 may also form a static sealing portion 99 or a support for the static seal 102, which directly or indirectly cooperates with the flared middle portion 52 of the transmission cup 38 and / or the joint of the protective sleeve 104 for attaching the transmission cup 38.

[0045] The internal structure 78 of the sealing device 66 includes a frame 782, preferably metal, which forms a shrink-fit support surface 72 and may also form a sealing seat 90. Alternatively, the sealing seat 90 may be formed on an annular component attached to the frame 782, which may or may not be made of a non-metallic material. Preferably, the internal structure 78 further includes a second component 784, which is fastened by any suitable means, specifically by bonding, overmolding, or mechanical fastening (e.g., by shrink-fitting or by fastening elements, or as...). Figures 1 to 3 The connecting portion 785, shown as being attached to the frame 782 via an elastic fastener, extends axially from the seal seat 90 in the axial reference direction D. The second component 784 may be made of plastic. It serves as a deflector plate, forms the blocking bend wall 92 of the internal structure, and, where appropriate, forms the static sealing portion 99 or support for the static seal 102, or even forms the static seal 102 itself. Figure 1 and Figure 2In the illustrated embodiment, the third component 786, together with the second component 784, defines an additional groove 106 near the sealing seat 90.

[0046] According to a variation not shown, the component forming the deflection plate can also form a sealing seat.

[0047] exist Figure 1 and Figure 2 In the illustrated embodiment, the internal structure 78 also supports a preferably annular encoder 108, which is positioned opposite the sidewall 824 or bottom 822 of the groove 82, and the encoder 108 may specifically be a multipole magnetic encoder or a sound wheel. With the sensor 110 partially inserted into the groove 82, the data encoded on the encoder 108 (specifically, position data) can be remotely read through the sidewall 824 of the groove 82. If the encoder 108 is positioned on a shrinkage assembly 88 of the internal structure 78, and if the shrinkage assembly is controlled to prevent uncontrollable deformation of the encoder 108, the reading can be radial. Alternatively, and preferably, the reading is axial, such as... Figure 1 and 2 As shown, in this configuration, the encoder 108 is supported by a flat annular flange 112 extending radially from the shrink fitting portion 88 toward the outer ring 20. It should be noted that even without the encoder 108, the flat annular flange 112, positioned opposite and shortly distanced from the sidewall 824, can be advantageous because it confines grease within the internal volume V, allowing for the elimination of one of the sealing lips 86 if necessary, and thus contributing to a reduction in frictional torque.

[0048] Figure 3 A variation of the sealing device 66 is shown, which is similar to... Figure 1 and Figure 2 The difference in the embodiment shown is that no encoder is used.

[0049] Figure 4 Another variant is shown, which is related to Figure 1 and Figure 2 The difference in the embodiment shown is that it has only one sealing lip 86.

[0050] Figure 5 Another variant is shown, which is related to Figure 1 and Figure 2 The difference in the embodiment shown is that the frame 762 of the external structure 76 of the sealing device consists of two parts 7621 and 7622, ​​which are fastened together by any suitable means (in this case by shrink fitting and mechanical interlocking).

[0051] According to a variant not shown, the sealing seat may have a flat annular surface parallel to the reference plane of the inner ring, and the external structure of the sealing device includes a sealing lip that axially abuts against the flat surface.

[0052] The examples shown in the accompanying drawings and discussed above are provided for illustrative purposes only. It is explicitly stated that it is possible to combine multiple illustrated embodiments to provide other embodiments. The described sealing device can be used in applications other than protecting wheel bearings and will be advantageously applicable to any sliding or rolling bearing, and particularly to any sliding or rolling bearing where the outer ring is intended to be fixed and the inner ring is intended to rotate. In a more general context, the first outer raceway 22, the second outer raceway 24, the first inner raceway 46, and the second inner raceway 62 will be referred to as guide raceways.

[0053] It should be emphasized that, as taught by those skilled in the art based on this disclosure, the accompanying drawings and the appended claims, all features, even those specifically described with respect to other features (alone or in any combination), can be combined with other features or groups of features disclosed herein, provided that they are not expressly excluded and there is no technical situation that makes such a combination impossible or meaningless.

Claims

1. A bearing (10), wherein, The bearing (10) is a sliding bearing or a rolling bearing and the bearing (10) includes at least one inner ring (36) and at least one outer ring (20), the inner ring (36) and the outer ring (20) being rotatable relative to each other about a rotation axis (XX) of the bearing (10), the inner ring (36) having a guide seat (62), and the outer ring (20) having at least one guide seat (24), the guide seat (24) of the outer ring (20) being positioned opposite to and relative to the guide seat (62) of the inner ring (36). The bearing (10) is defined by the following elements: the inner ring (36) has a second axial end wall (74) facing an axial reference direction (D) parallel to the axis of rotation (XX), the second axial end wall (74) being axially located at a distance from the guide ring (62) of the inner ring (36) along the axial reference direction (D), the inner ring (36) having a shrink-fit support surface (72), the shrink-fit support surface (72) being axially located between the second axial end wall (74) and the guide ring of the inner ring (36). Between (62), the bearing (10) includes a sealing device (66), the sealing device (66) including at least an outer structure (76) and an inner structure (78), the outer structure (76) being secured to the outer ring, the inner structure (78) being secured to the inner ring (36), the outer structure (76) and the inner structure (78) together defining a sealing volume (L) leading to the internal volume (V) of the bearing (10), the inner structure (78) including a shrink fitting portion (88) and at least one sealing seat (90), the shrink fitting portion (88) shrink fitting On the shrink-fit support surface (72) of the inner ring (36), the outer structure (76) includes at least one sealing lip (86) that slides against the sealing seat (90), the sealing seat (90) and the sealing lip (86) sealing the sealing volume (L), the sealing seat (90) being axially located at a distance from the second axial end wall (74) of the inner ring (36) along the axial reference direction (D), and the sealing seat (90) being closer to the axis of rotation (XX) than the shrink-fit support surface (72), characterized in that, - The sealing seat (90) is radially away from the rotation axis (XX) of the bearing (10). - The internal structure (78) further includes a connecting portion (785) and a deflecting plate, the connecting portion (785) projecting axially relative to the sealing seat (90) in the axial reference direction (D), and the deflecting plate (784) projecting radially from the connecting portion in a radial direction opposite to the rotation axis (XX). - The deflection plate and the external structure (76) form a blocking bend channel (S) leading to the sealing volume (L), the blocking bend channel (S) having an inlet (E) further away from the axis of rotation (XX) than the sealing seat (90), the sealing seat (90) and the sealing lip (86) being positioned in the sealing volume (L) and between the blocking bend channel (S) and the internal volume (V) of the bearing (10).

2. The bearing (10) according to claim 1, characterized in that, The sealing seat (90) is closer to the axis of rotation (XX) than the bottom (FI) of the guide ring (62) of the inner ring (36).

3. The bearing (10) according to any one of claims 1-2, characterized in that, The shrinkage assembly support surface (72) of the inner ring (36) is radially away from the rotation axis (XX) of the bearing (10).

4. The bearing (10) according to any one of claims 1-2, characterized in that, The external structure (78) includes a frame (782) that forms the shrink assembly portion (88) and the sealing seat (90).

5. The bearing (10) according to claim 4, characterized in that, The deflection plate is attached to the frame (782) by fastening, shrink fitting, bonding, fastening elements or any other means.

6. The bearing (10) according to any one of claims 1-2, characterized in that, The internal structure (78) includes a static sealing portion (99) that supports and abuts against a static seal (102) which is intended to be located between the internal structure (78) and a component secured to the inner ring (36), specifically a drive cup (38) or a sleeve protecting the drive cup (38).

7. The bearing (10) according to any one of claims 1-2, characterized in that, The internal structure includes an encoder (108).

8. The bearing (10) according to any one of claims 1-2, characterized in that, The guide ring (24) of the outer ring (20) is a raceway, the guide ring (62) of the inner ring (36) is a raceway, the bearing (10) is a rolling bearing, the rolling bearing includes at least one row of second rolling elements (18) capable of rolling on the raceway (24) of the outer ring (20) and the raceway (62) of the inner ring (36) to allow relative rotational movement about the axis of rotation (XX) between the inner ring (36) and the outer ring (20).

9. The bearing according to claim 8, characterized in that, The sealing seat (90) is closer to the axis of rotation (XX) than the pitch circle (C) defined by the at least one row of second rolling elements (18).

10. A vehicle wheel support device, characterized in that, The vehicle wheel support device includes a bearing (10) according to any one of the preceding claims, the inner ring (36) being a rotating ring, and the outer ring (20) being a fixed ring having a joint (28) for fastening to a wheel support (30).

11. The vehicle wheel support device according to claim 10, characterized in that, The inner ring (36) is the wheel hub (34) or the inner ring (36) secured to the wheel hub (34).

12. The vehicle wheel support device according to claim 10, characterized in that, The wheel support (30) is the wheel pivot.

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