Plain bearing or rolling bearing with a sealing device, equipped with a seal seat closer to the axis of rotation.

Abstract

To provide a sliding bearing or rolling bearing which combines a satisfactory sealing function and a large pitch circle diameter from the viewpoints of technical performance and monetary cost. A bearing (10) includes an inner ring (36), an outer ring (20), and a sealing device (66). The sealing device (66) includes at least an outer structure (76) fixed to the outer ring (20) and an inner structure (78) fixed to the inner ring (36). The inner structure (78) has a shrink-fit portion (88) shrink-fitted to a shrink-fit support surface (72) of the inner ring (36) and at least one seal seat (90). The outer structure (76) has at least one seal lip (86) that slides against the seal seat (90). The seal seat (90) is provided at a distance in the axial direction from an end wall (74) of the inner ring (36) and is closer to the rotation axis (XX) than the shrink-fit portion (72).

Description

Technical Field

[0001] The present invention relates to a sliding bearing or a rolling bearing, and more particularly to a rolling bearing for a wheel of a motor vehicle, preferably a rolling bearing for a steering drive wheel (however, it is not limited thereto).

Background Art

[0002] In some electric or hybrid drive trains of motor vehicles, the space available for installing the transmission bowl of the drive wheel is limited. Therefore, an assembly has been proposed in which at least a part of the rotation guide of the wheel overlaps with the transmission bowl, such as the type described in French Patent Application No. 2000720, which is not yet published at present. Such an assembly requires a wheel bearing with a larger diameter than those commonly available on the market. To ensure the sealing performance of such a bearing, it is necessary to provide a seal. For this purpose, a cassette seal housed in the space directly located between the inner and outer rings in the radial direction can naturally be considered. However, such a large-diameter seal causes problems that are difficult to solve without increasing the functional cost. Specifically, such a seal causes friction between the seal lip and the seat, and this friction increases as the diameter increases, adversely affecting the resistance torque and the operating temperature. On the other hand, larger-diameter joints require even higher assembly accuracy and stricter manufacturing tolerances. Finally, in order to insert the cassette seal into the wheel bearing, two cylindrical seats facing each other are required on the outer and inner rings.

[0003] U.S. Patent No. 9,377,055 (Patent Document 1) describes a wheel bearing with a sealing device consisting of a general cassette seal protected by a baffle seal. In this sealing device, an outer structure fixed to the outer ring of the bearing is positioned opposite an inner structure fixed to the inner ring of the bearing, and these two inner and outer structures are not in contact with each other. Here again, in order to insert the cassette seal into the wheel bearing, two cylindrical support surfaces facing each other are required on the outer and inner rings.

[0004] Japanese Patent Publication No. 2008-138766 (Patent Document 2) is the basis for the premise of claim 1 and describes a wheel bearing with a sealing device. The sealing device includes an outer structure fixed to the outer ring of the bearing and an inner structure fixed to the inner ring of the bearing, the outer and inner structures together defining a sealed space, the inner structure having a shrink-fit portion and at least one seal seat portion that is shrink-fitted to the shrink-fit support surface of the inner ring, and the outer structure having at least one seal lip that slides against the seal seat portion to seal the sealed space. The seal seat portion is flat and extends in the direction of the rotation axis so as to cover a portion of the axial end face of the inner ring. In such a device, the seal and the seal seat portion are directly exposed to dirt. The seal seat portion that rotates with the inner ring acts centrifugal force on the dirt, causing the dirt to be blown in the direction of the seal, which is undesirable.

[0005] International Publication No. 2008 / 102579 (Patent Document 3) describes a wheel bearing equipped with a sealing device, which includes an outer structure fixed to the outer ring of the bearing and an inner structure fixed to the inner ring of the bearing, and these outer and inner structures together define a sealed space that opens into the internal space of the bearing. The inner structure has a shrink-fit portion that is shrink-fitted to the shrink-fit support surface of the inner ring and at least one seal seat portion. The outer structure has at least one seal lip that slides against the seal seat portion to seal the sealed space. The seal seat portion has a cylindrical portion that faces radially outward and covers the shrink-fit portion, and a flat portion that extends from the cylindrical portion in the opposite direction to the rotation axis. The resulting structure has a large number of parts and is complex to assemble. Also, because the seal seat portion is located radially outward from the shrink-fit support surface of the inner structure, it is not suitable for large-diameter wheel bearings. [Prior art documents] [Patent Documents]

[0006] [Patent Document 1] U.S. Patent No. 9377055 [Patent Document 2] Japanese Patent Publication No. 2008-138766 [Patent Document 3] International Publication No. 2008 / 102579 [Overview of the Initiative] [Problems that the invention aims to solve]

[0007] The object of the present invention is to improve upon the shortcomings of the prior art and provide a sliding bearing or rolling bearing that achieves both satisfactory sealing function and a large pitch circle diameter in terms of technical performance and cost. [Means for solving the problem]

[0008] For this purpose, in a first aspect of the present invention, a sliding bearing or rolling bearing comprising at least one inner ring, at least one outer ring, and a sealing device, wherein the inner ring and the outer ring are rotatable relative to each other about the rotation axis of the bearing, the inner ring has a guide race, and the outer ring has at least one guide race positioned opposite to the guide race of the inner ring and jointly defining the internal space of the bearing with the guide race of the inner ring, the inner ring has an axial end face oriented in a reference axis direction parallel to the rotation axis, the axial end face is provided at an axial distance from the guide race of the inner ring in the reference direction, and the inner ring is provided between the axial end face and the guide race of the inner ring in the axial direction A bearing is proposed in which the seal device has a shrink-fit support surface, and the sealing device includes at least an outer structure fixed to the outer ring and an inner structure fixed to the inner ring, the outer structure and the inner structure together define a sealed space opening into the internal space of the bearing, the inner structure has a shrink-fit portion shrink-fitted to the shrink-fit support surface of the inner ring and at least one seal seat portion, the outer structure has at least one seal lip sliding in contact with the seal seat portion, and the seal seat portion and the seal lip seal the sealed space, wherein the seal seat portion is provided at an axial distance from the end wall of the inner ring in the reference axis direction and is closer to the shrink-fit support surface with respect to the axis of rotation.

[0009] According to the present invention, the seal seat portion faces radially opposite to the rotation axis of the bearing. The inner structure further has a connecting portion that protrudes axially from the seal seat portion in the reference direction, and a deflector that protrudes radially from the connecting portion radially opposite to the rotation axis. The deflector, together with the outer structure, forms a baffle passage that opens into the sealed space, and the baffle passage has an entrance that is further away from the rotation axis than the seal seat portion, and the seal seat portion and the seal lip are located in the sealed space and interposed between the baffle passage and the internal space of the bearing. Due to its geometry, the baffle passage is designed to easily apply centrifugal force to any dirt that may enter the baffle passage.

[0010] By positioning the seal seat outside the inner ring, the diameter and outer circumference of the seal seat can be reduced, and the friction torque between the seal lip and the seal seat is suppressed, which is a significant advantage for bearings with a large pitch circle diameter.

[0011] Preferably, the seal seat is located closer to the bottom of the guide race of the inner ring than to the axis of rotation.

[0012] In one embodiment, the cylindrical shrink-fit support surface of the inner ring faces radially opposite to the rotation axis of the bearing.

[0013] In one embodiment, the inner structure has a frame that forms the shrink-fit portion and the seal seat portion.

[0014] Preferably, the deflector is attached to the frame by fastening, shrink-fitting, or adhesive using a retaining element or any other means.

[0015] In one embodiment, the inner structure has a static sealing portion that contacts a static seal intended to be interposed between the inner structure and a component fixed to the inner ring, particularly a transmission bowl or a bellows protecting the transmission bowl. This static seal can protect the connection between the inner ring and the component to which the inner ring is attached.

[0016] In one embodiment, the inner structure has an encoder. This encoder enables the encoding of information read by a sensor, preferably a sensor stationary to the outer structure, particularly positional information.

[0017] In one embodiment, the guide race of the outer ring is a raceway, the guide race of the inner ring is a raceway, and the bearing is a rolling bearing that includes at least one row of rolling elements capable of rolling on the raceways of the outer ring and the inner ring such that the inner ring and the outer ring can rotate relative to each other around the axis of rotation. Here, according to the present invention, the pitch circle diameter of the rolling bearing can be increased without adversely affecting the resistance torque of the rolling bearing. Preferably, the seal seat portion is closer to the pitch circle formed by the row of rolling elements when viewed from the axis of rotation. By reducing the outer circumference of the seal seat portion in this way, the friction torque of the bearing is suppressed.

[0018] Another aspect of the present invention relates to a wheel support device for a motor vehicle, comprising a bearing as described in any one of the preceding claims, wherein the inner ring is a rotating ring, preferably a hub ring or a ring fixed to a hub ring, and the outer ring is a fixed ring having a connecting portion for attachment to a wheel support, in particular a wheel pivot.

[0019] Other features and advantages of the present invention will become apparent from the following description, with reference to the accompanying drawings. [Brief explanation of the drawing]

[0020] [Figure 1] It is an axial sectional view of a wheel support assembly provided with a wheel bearing according to a first embodiment of the present invention. [Figure 2] It is a detailed view of some components of the wheel bearing in FIG. 1. [Figure 3] It is a detailed view of some components of a wheel bearing according to a second embodiment of the present invention. [Figure 4] It is a detailed view of some components of a wheel bearing according to a third embodiment of the present invention. [Figure 5] It is a detailed view of some components of a wheel bearing according to a fourth embodiment of the present invention.

Mode for Carrying Out the Invention

[0021] For the sake of clarity, all identical or similar components are identified by the same reference numerals throughout all the figures.

[0022] FIG. 1 shows a drive wheel assembly 10 of a motor vehicle, which is intended to be fixed to a suspension member of a motor vehicle (not shown) and defines a rotation axis XX, a rotation sub-assembly 14 that can rotate about the rotation axis XX inside the fixed sub-assembly 12, and guide rolling elements 16, 18 between the rotation sub-assembly 14 and the fixed sub-assembly 12.

[0023] The fixed subassembly 12 in this example is composed of a solid, single-piece metal outer ring 20. In this embodiment, the outer ring 20 has two coaxial outer raceways 22, 24 that define the axis of rotation XX, one of which is intended to be located on the outer side of the vehicle, and the other outer raceway 24 is intended to be located on the inner side of the vehicle, i.e., closer to the central plane in the longitudinal and vertical directions of the vehicle. The outer ring further has at least one mounting clamp portion 26 that extends radially outward. The mounting clamp portion 26 has a hole 28 formed therein for attaching the mounting clamp portion 26 to a suspension member 30 (a strut pivot in this example) by a mounting element 32.

[0024] The rotating subassembly 14 includes a hub ring 34 that forms an inner ring on the outer side of the vehicle, a second inner ring 36 on the inner side of the vehicle, and a transmission bowl 38.

[0025] The hub wheel 34 is a solid, single-piece metal component having a flange 40 for mounting the rim and brake disc of the drive wheel. The flange 40 has a flat surface 42 that contacts the brake disc or the rim of the wheel. The flange 40 is also provided with mounting holes 44 into which the mounting elements of the rim and / or brake disc can be inserted. The hub wheel 34 has a first inner raceway 46 opposite to a first outer raceway 22.

[0026] The transmission bowl 38 is a solid, single-piece metal component. In this embodiment, the transmission bowl 38 has a solid protruding end 50 and a flared central portion 52 defining a cavity 54, and functions as a constant velocity joint. The protruding portion 50 of the transmission bowl 38 is splined and is fitted into the splined tubular cavity 56 of the hub ring 34 by gap fit, interlock fit, or compression fit to form a splined contact connection. Furthermore, Figure 1 shows a nut 58 as a means for attaching the transmission bowl 38 to the hub ring 34, which is screwed onto the threaded end of the protruding portion 50 and pressed against the shoulder of the hub ring 34. The inner bearing ring 36 on the vehicle side is shrink-fitted to the cylindrical shrink-fit surface 60 of the hub ring 34 and is sandwiched axially between the hub ring 34 and the transmission bowl 38.

[0027] The inner ring 36 of the rolling bearing has an inner raceway 62 formed on the inner side of the vehicle, opposite to the outer raceway 24. The rolling elements 16 and 18 consist of a first row of rolling elements 16 that roll on the outer raceway 22 and inner raceway 46 on the outer side of the vehicle, and a second row of rolling elements 18 that roll on the outer raceway 24 and inner raceway 62 on the inner side of the vehicle.

[0028] These two rows of rolling elements 16, 18 and the tracks 22, 24, 46, 62 are protected by two sealing devices: a sealing device 64 located on the outer side of the vehicle between the outer ring 20 and the hub ring 34, and a sealing device 66 located on the inner side of the vehicle between the outer ring 20 and the inner bearing ring 36.

[0029] The components of the wheel bearing 10 described above are general and can take on various different forms. Specifically, the inner raceway 46 may be formed on a bearing ring attached to the hub ring 34. The inner ring 36 on the inner side of the vehicle may be fixed to the hub ring 34 by a snap ring and, if necessary, may be kept away from contact with the transmission bowl 38. The transmission bowl 38 may be attached to the hub ring 34 by any means. The bearing may also have a single row of rolling elements 16, which may be balls or rollers.

[0030] Next, we consider the sealing device 66 located on the inner side of the vehicle, as detailed in Figure 2. The sealing device 66 seals the space between the bearing outer ring 20 and the bearing inner ring 36, and more specifically, protects the space V located between the raceway 24 of the outer ring 20 and the raceway 62 of the inner ring 36. In this region, the bearing outer ring 20 has a shrink-fit surface 68 which is cylindrical in this example and faces the rotation axis XX, and an end wall 70 which is perpendicular to the rotation axis XX and tangent to the end face 70, allowing a reference plane PE of the bearing outer ring 20 to be defined. The shrink-fit surface 68 extends axially and circumferentially in the region of the outer ring 20 located between the raceway 24 and the end face 70 on the inner side of the vehicle. The shrink-fit surface 68 of the outer ring is located further from the rotation axis XX than the pitch circle C of the rows of rolling elements 18, and in this embodiment, further from the rotation axis XX than the raceway bottom FE of the raceway 24 of the outer ring 20.

[0031] The inner ring 36 of the bearing also has a shrink-fit surface 72 facing radially outward, which is cylindrical in this example, and an end wall 74 that is perpendicular to the rotation axis XX and in contact with the end face 74, defining the reference plane PI of the inner ring 36. The shrink-fit surface 72 extends in the axial and circumferential directions in the region of the inner ring located between the raceway 62 on the inner side of the vehicle and the end face 74. The end face 74 of the inner ring and the end face 70 of the outer ring of the bearing face are oriented in a common direction D (hereinafter referred to as the reference axis direction) parallel to the reference axis XX. In this embodiment, the reference plane PI of the inner ring 36 is located at a distance from the reference plane PE of the outer ring 20 of the bearing, and is shifted in the reference axis direction D. As a result, the inner ring 36 protrudes further in the reference axis direction D than the outer ring 20 of the bearing, passing over the reference plane PE of the outer ring 20. More specifically, at least a portion of the shrink-fit surface 72 of the inner ring 36 of the bearing is positioned on one side with respect to the reference plane PE of the outer ring 20 of the bearing, facing the shrink-fit surface 68 of the outer ring 20.

[0032] The sealing device 66 includes an outer structure 76 integrated with the outer ring 20, and an inner structure 78 integrated with the inner ring 36.

[0033] The outer structure 76 has a shrink-fit portion 80 that is shrink-fitted to the shrink-fit surface 68 of the outer ring 20, and functional portions that constitute a radially outward-opening gutter 82, a baffle wall 84, and two seal lips 86 in this embodiment. The gutter 82 has a bottom portion 822 and side walls 824, the side walls 824 being located on each axial side of the bottom portion and further away from the bottom portion with respect to the axis of rotation. In this embodiment, the outer structure 76 has a rigid frame 762 made of, for example, sheet metal or plastic, and an overmolded portion 764. The frame 762 forms the shrink-fit portion 80 and the gutter 82, while the overmolded portion 764 forms the baffle wall 84 and the seal lip 86.

[0034] The inner structure 78 has a shrink-fit portion 88 that is shrink-fitted onto the shrink-fit support surface 72 of the inner ring 36, and functional portions that constitute a seal seat portion 90 and a baffle wall 92. The baffle wall 92 is positioned opposite the baffle wall 84 of the outer structure 76 so as to define a baffle passage S between the inner structure 78 and the outer structure 76. The seal lip 86 is elastically deformable and contacts the seal seat portion 90, which is cylindrical in this embodiment. The inner structure 78 and the outer structure 76 of the sealing device jointly define an annular housing portion L for the seal seat portion 90 and the seal lip 86. The baffle passage S opens into the annular housing portion L, and the internal space V defined by the raceway 24 of the bearing outer ring 20 and the raceway 62 of the bearing inner ring 36 is also in communication with it.

[0035] The shrink-fit portion 88 and the functional portion of the inner structure 78 are positioned on each side of the reference plane PI of the inner ring 36. This makes it possible to position the seal seat portion 90 closer to the rotation axis XX than the shrink-fit portion 88. This arrangement minimizes the diameter of the seal seat portion 90, thereby minimizing the friction torque between the seal lip 86 and the seal seat portion 90, and reducing the heat generated by this friction.

[0036] The baffle passage S has an inlet E defined by the inlet of the baffle wall 84 of the outer structure 76 and the inlet of the baffle wall 92 of the inner structure 78. The inlet E of the baffle passage S and the shrink-fit portion 80 of the outer structure 76 are located on each axial side of the gutter 82. The baffle passage S and the gutter 82 are located on the same side with respect to the reference plane PE of the outer ring 20, and on the opposite side with respect to the reference plane PE from the side where the shrink-fit portion 80 of the outer structure 76 is located. The inlet of the baffle passage is located further away from the seal seat portion 90 with respect to the rotation axis XX.

[0037] The baffle wall 84 of the outer structure 76 is formed by annular ribs 94 projecting axially toward the baffle wall 92 of the inner structure 78. Similarly, the baffle wall 92 of the inner structure 78 is formed by one or more annular ribs 96, one or more annular ribs 96 projecting axially toward the baffle wall 84 of the outer structure 76 and positioned in the space between the annular ribs 94 of the outer structure 76. The annular ribs 94 of the outer structure 76 form one or more further gutters 98 located inside the baffle passage S. The baffle wall 92 has a frustoconical surface 922 facing toward the axis of rotation and a frustoconical wall 924 facing radially outward at the locations of the annular ribs 96 of the inner structure 78.

[0038] The inlet E of the baffle passage S is annular and faces the bearing outer ring 20 in an axial direction opposite to the reference axis direction D. The inlet E is located further away from the bottom 822 of the gutter 82 as viewed from the rotation axis XX. In this example, preferably, the inlet E is located further away from the rotation axis XX than the pitch circle C formed by the rows of rolling elements 18.

[0039] Preferably, the inlet portion of the baffle wall 92 of the inner structure 78 is frustoconical in shape, as shown in the figure, converging toward a vertex that is further away from the inlet E when viewed from the reference plane PE of the outer ring. Similarly, preferably, the inlet portion of the baffle wall 84 of the outer structure 76 is frustoconical in shape, as shown in the figure, converging toward a vertex that is further away from the inlet E when viewed from the reference plane PE of the outer ring.

[0040] In this embodiment, it can be seen that the gutter 82 overlaps at least partially in the axial direction with the shrink-fit surface 72 of the bearing inner ring 36 and the shrink-fit portion 88 of the inner structure 78. The baffle wall 84 of the outer structure 76 is entirely located on one side of the reference plane PI of the bearing inner ring 36 and entirely located on one side of the gutter 82. Therefore, the gutter 82 is located in the axial direction between the shrink-fit portion 80 of the outer structure 76 and the baffle wall 84 of the outer structure 76.

[0041] Although the configuration is arbitrary, the functional portion of the inner structure 78 may further constitute a seat 99 or support for a static seal 102 that directly or indirectly cooperates with the flared central portion 52 of the transmission bowl 38, and / or a connection for attaching the protective sleeve 104 of the transmission bowl 38.

[0042] The inner structure 78 of the sealing device 66 has a frame 782, which is preferably made of metal. The frame 782 forms a shrink-fit portion 72, which may also form a seal seat portion 90. Alternatively, the seal seat portion 90 may be formed on an annular component attached to the frame 782, which may be made of a metallic or non-metallic material. Preferably, the inner structure 78 further has a second component 784 attached to the connecting portion 785 of the frame 782 by any suitable means, in particular, adhesive, overmolding or mechanical fastening, e.g., shrink-fit, fastening element, or elastic fastening as shown in Figures 1 to 3. In this example, the connecting portion 785 of the frame 782 protrudes axially from the seal seat portion 90 in the reference direction D. The second component 784 may be made of plastic. The second component 784 functions as a deflector, forming the baffle wall 92 of the inner structure, and optionally forming a seat 99 or support for the static seal 102, or the static seal 102 itself. In the embodiments shown in Figures 1 and 2, the third component 786, in conjunction with the second component 784, forms an additional gutter 106 near the seal seat 90.

[0043] As one modified example not shown, the component constituting the deflector may also have a seal seat portion formed therein.

[0044] In the embodiments shown in Figures 1 and 2, the inner structure 78 further supports a preferably annular encoder 108 positioned opposite the side wall 824 or bottom 822 of the gutter 82. Specifically, the encoder 108 may be a multipole magnetic encoder or a tone wheel. A sensor 110 that locally penetrates into the gutter 82 may remotely read the data encoded by the encoder 108, particularly position data, through the wall 824 of the gutter 82. The reading may be radial if the encoder 108 is installed in a shrink-fit portion 88 of the inner structure 78 and the shrink-fit is controlled so as not to deform the encoder 108 uncontrollably. Alternatively, and preferably, the reading may be axial, as shown in Figures 1 and 2. In this case, the encoder 108 is supported by an annular flat flange 112 projecting radially from the shrink-fit portion 88 toward the bearing outer ring 20. Furthermore, even in the absence of the encoder 108, the annular flat flange 112, positioned at a short distance from the side wall 824 and facing the side wall 824, can contain the grease within the space V, and if necessary, one of the seal lips 86 can be eliminated, which can be advantageous in that it contributes to reducing friction torque.

[0045] Figure 3 shows a modified example of the sealing device 66, where an encoder is not used in the embodiment shown in Figures 1 and 2.

[0046] Figure 4 shows a further modification in which the seal shape differs from that of the embodiments shown in Figures 1 and 2. In this modification, there is only one seal lip 86.

[0047] Figure 5 shows another variation in which the frame 762 of the outer structure 76 of the sealing device in the embodiments shown in Figures 1 and 2 is composed of two parts 7621 and 7622 fastened to each other by any suitable means (in this example, shrink-fit and mechanical interlocking).

[0048] As an example of a modified form not shown, the seal seat portion may have an annular flat surface parallel to the reference plane of the inner ring, in which case the outer structure of the sealing device will have a seal lip that is axially tangent to the flat surface.

[0049] The illustrations and the examples described above are for illustrative purposes only. It should be noted that other embodiments can be provided by combining the various embodiments shown in the illustrations. The described sealing device can be applied to applications other than the protection of wheel bearings, and can be advantageously applied to any sliding bearing or rolling bearing, in particular, any sliding bearing or rolling bearing intended to have the outer ring on the stationary side and the inner ring on the rotating side. For general purposes, raceways 22, 24, 46, and 62 are referred to as guide races.

[0050] All configurations taught to those skilled in the art from the contents, drawings, and attached claims of this disclosure are described in detail in relation to other specified configurations, but we would like to emphasize that they may be combined with other configurations or sets of configurations disclosed herein, either individually or in any combination, as long as they are not explicitly excluded or are technically impossible or unreasonable. Furthermore, this disclosure includes the following details regarding the manner of implementation. [Aspect 1] At least one inner ring (36), At least one outer ring (20) and Sealing device (66), A sliding bearing or rolling bearing (10) having the following: The inner ring (36) and the outer ring (20) are rotatable relative to each other about the rotation axis (XX) of the bearing (10), the inner ring (36) has a guide race (62), and the outer ring (20) has at least one guide race (24) positioned opposite to the guide race (62) of the inner ring (36) and jointly defining the internal space (V) of the bearing (10) with the guide race (62) of the inner ring (36), and the inner ring (36) is front The inner ring (36) has an axial end face (74) oriented in a reference axis direction (D) parallel to the rotation axis (XX), the axial end face (74) is provided at an axial distance from the guide race (62) of the inner ring (36) in the reference direction (D), the inner ring (36) has a shrink-fit support surface (72) provided in the axial direction between the axial end face (74) and the guide race (62) of the inner ring (36), and the sealing device (66) has at least, The bearing (10) includes an outer structure (76) fixed to the outer ring and an inner structure (78) fixed to the inner ring (36), wherein the outer structure (76) and the inner structure (78) jointly define a sealed space (L) that opens into the internal space (V) of the bearing (10), and the inner structure (78) has a shrink-fit portion (88) that shrink-fits onto the shrink-fit support surface (72) of the inner ring (36) and at least one seal seat portion (90), and the outer structure In a bearing (10), (76) has at least one seal lip (86) that slides against the seal seat portion (90), and the seal seat portion (90) and the seal lip (86) seal the sealed space (L), and the seal seat portion (90) is provided at an axial distance from the end wall (74) of the inner ring (36) in the reference axis direction (D) and is closer to the shrink-fit support surface (72) with respect to the rotation axis (XX), - The seal seat portion (90) faces radially opposite to the rotation axis (XX) of the bearing (10), -The inner structure (78) further has a connecting portion (785) that protrudes axially from the seal seat portion (90) in the reference direction (D), and a deflector (784) that protrudes radially from the connecting portion on the radially opposite side from the rotation axis (XX), - The deflector (784), together with the outer structure (76), forms a baffle passage (S) that opens into the sealed space (L), the baffle passage (S) having an entrance (E) that is further away from the seal seat portion (90) as seen from the rotation axis (XX), the seal seat portion (90) and the seal lip (86) are located within the sealed space (L) and interposed between the baffle passage (S) and the internal space (V) of the bearing (10), the bearing (10). [Aspect 2] A bearing (10) according to Embodiment 1, characterized in that the seal seat portion (90) is closer to the bottom portion (FI) of the guide race (62) of the inner ring (36) than the rotation axis (XX). [Aspect 3] A bearing (10) according to embodiment 1 or 2, characterized in that the cylindrical shrink-fit support surface (72) of the inner ring (36) faces radially opposite to the rotation axis (XX) of the bearing (10). [Aspect 4] A bearing (10) according to any one of embodiments 1 to 3, characterized in that the inner structure (78) has a frame (782) that forms the shrink-fit portion (88) and the seal seat portion (90). [Aspect 5] The bearing (10) according to embodiment 4, characterized in that the deflector (784) is attached to the frame (782) by fastening with a retaining element or any other means, shrink fitting, or adhesive bonding. [Aspect 6] A bearing (10) according to any one of embodiments 1 to 5, wherein the inner structure (78) has a static sealing portion (99) that contacts a static seal (102) intended to be interposed between the inner structure (78) and a component fixed to the inner ring (36), in particular the transmission bowl (38) or a bellows (104) protecting the transmission bowl (38), the bearing (10). [Aspect 7] A bearing (10) according to any one of embodiments 1 to 6, characterized in that the inner structure has an encoder (108). [Aspect 8] A bearing (10) according to any one embodiment of embodiments 1 to 7, characterized in that the guide race (24) of the outer ring (20) is a raceway, the guide race (62) of the inner ring (36) is a raceway, and the bearing (10) is a rolling bearing comprising at least one row of rolling elements (18) that can roll on the raceway (24) of the outer ring (20) and the raceway (62) of the inner ring (36) so that the inner ring (36) and the outer ring (20) can rotate relative to each other about the rotation axis (XX). [Aspect 9] A bearing according to embodiment 8, characterized in that the seal seat portion (90) is closer to the pitch circle (C) formed by the row of rolling elements (18) when viewed from the rotation axis (XX). [Aspect 10] The bearing (10) is provided according to any one of the embodiments 1 to 9, A wheel support device for a motor vehicle, characterized in that the inner ring (36) is a rotating ring, preferably a hub ring (34) or a ring (36) fixed to a hub ring (34), and the outer ring (20) is a fixed ring having a connecting portion (28) for fastening and fixing to a wheel support (30), particularly a wheel pivot.

Claims

1. At least one inner ring (36) and At least one outer ring (20) and A sealing device (66), A sliding bearing or rolling bearing (10) comprising, The inner ring (36) and the outer ring (20) are rotatable relative to each other about the rotation axis (XX) of the bearing (10), the inner ring (36) has a guide race (62), and the outer ring (20) has at least one guide race (24) positioned opposite to the guide race (62) of the inner ring (36) and jointly defining the internal space (V) of the bearing (10) with the guide race (62) of the inner ring (36), and the inner ring (36) is The inner ring (36) has an axial end face (74) facing a reference axis direction (D) parallel to the rotation axis (XX), the axial end face (74) is provided at an axial distance from the guide race (62) of the inner ring (36) in the reference axis direction (D), the inner ring (36) has a shrink-fit support surface (72) provided in the axial direction between the axial end face (74) and the guide race (62) of the inner ring (36), and the sealing device (66) is at least, The bearing (10) includes an outer structure (76) fixed to the outer ring and an inner structure (78) fixed to the inner ring (36), wherein the outer structure (76) and the inner structure (78) jointly define a sealed space (L) that opens into the internal space (V) of the bearing (10), and the inner structure (78) has a shrink-fit portion (88) that is shrink-fitted to the shrink-fit support surface (72) of the inner ring (36) and at least one seal seat portion (90), and the outer structure (7 6) The bearing (10) has at least one seal lip (86) that slides against the seal seat portion (90), the seal seat portion (90) and the seal lip (86) seal the sealed space (L), and the seal seat portion (90) is provided at an axial distance from the axial end face (74) of the inner ring (36) in the reference axis direction (D), and is closer to the shrink-fit support surface (72) when viewed from the rotation axis (XX), - The seal seat portion (90) faces radially opposite to the rotation axis (XX) of the bearing (10), - The inner structure (78) further has a connecting portion (785) that protrudes axially from the seal seat portion (90) in the reference axis direction (D), and a deflector (784) that protrudes radially from the connecting portion on the radially opposite side from the rotation axis (XX), - The deflector (784), together with the outer structure (76), forms a baffle passage (S) that opens into the sealed space (L), the baffle passage (S) having an entrance (E) that is further away from the seal seat portion (90) as viewed from the rotation axis (XX), the seal seat portion (90) and the seal lip (86) being located within the sealed space (L) and interposed between the baffle passage (S) and the internal space (V) of the bearing (10), characterized in that the bearing (10).

2. The bearing (10) according to claim 1, characterized in that the seal seat portion (90) is closer to the bottom portion (FI) of the guide race (62) of the inner ring (36) when viewed from the rotation axis (XX).

3. A bearing (10) according to claim 1 or 2, characterized in that the cylindrical shrink-fit support surface (72) of the inner ring (36) faces radially opposite to the rotation axis (XX) of the bearing (10).

4. A bearing (10) according to any one of claims 1 to 3, characterized in that the inner structure (78) has a frame (782) that forms the shrink-fit portion (88) and the seal seat portion (90).

5. The bearing (10) according to claim 4, characterized in that the deflector (784) is attached to the frame (782) by fastening with a retaining element, shrink fitting, or adhesive bonding.

6. A bearing (10) according to any one of claims 1 to 5, wherein the inner structure (78) has a static sealing portion (99) that contacts a static seal (102) intended to be interposed between the inner structure (78) and a component fixed to the inner ring (36).

7. A bearing (10) according to any one of claims 1 to 6, characterized in that the inner structure has an encoder (108).

8. A bearing (10) according to any one of claims 1 to 7, wherein the guide race (24) of the outer ring (20) is a raceway, the guide race (62) of the inner ring (36) is a raceway, and the bearing (10) is a rolling bearing comprising at least one row of rolling elements (18) that can roll on the raceway (24) of the outer ring (20) and the raceway (62) of the inner ring (36) such that the inner ring (36) and the outer ring (20) can rotate relative to each other about the rotation axis (XX).

9. A bearing according to claim 8, characterized in that the seal seat portion (90) is closer to the pitch circle (C) formed by the row of rolling elements (18) when viewed from the rotation axis (XX).

10. The bearing (10) is provided according to any one of claims 1 to 9, A wheel support device for a motor vehicle, characterized in that the inner ring (36) is a rotating wheel, and the outer ring (20) is a fixed wheel having a connecting portion (28) for fastening and fixing to a wheel support (30).

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