WHEEL BEARING EQUIPPED WITH A SEALING DEVICE WITH GUTTER AND CHICANE

A wheel bearing (10) is provided with a sealing device (66) comprising at least an outer structure (76) and an inner structure (78) together delimiting a chicane passage(S) having an inlet (E). The outer structure (76) forms an annular gutter (82) which is open radially outwards. The inlet (E) of the chicane passage (S) and the shrink-fitting portion (80) of the outer structure (76) are situated axially on either side of the gutter (82). The shrink-fitting portion (80) of the outer structure (76) is situated on one side of a reference plane (PE) of the outer ring (20), perpendicular to the axis of revolution (XX) and tangential to the end wall (70) of the outer ring (20) opposite to the chicane passage (S) and to the gutter (82).

TECHNICAL FIELD OF THE INVENTION

The invention relates to a wheel bearing, in particular a motor vehicle wheel bearing, and in particular, although not exclusively, to a drive wheel bearing.

STATE OF THE PRIOR ART

The electric or hybrid drivetrains of certain motor vehicles reduce the space available for positioning the torque converter of the drive wheels, and have led to the proposal of assemblies in which at least part of the rotational guidance of the wheels overlaps with the torque converter, of the type described for example in the French application FR2000720, unpublished to date. Such assemblies require larger-diameter wheel bearings than those normally found on the market. To guarantee the sealing of such bearings, it is necessary to provide seals. For this purpose, a cassette seal can naturally be considered, housed in a space situated radially directly between the inner and outer ring. However, such a large-diameter seal poses problems that are difficult to solve without increasing the cost of the function. In particular, the seal generates friction between the seal lip and the seat, and this friction increases with diameter, which has a negative impact on resistive torque and operating temperature. On the other hand, a large-diameter joint requires additional assembly precision and reduced manufacturing tolerances. Finally, inserting a cassette seal into the wheel bearing requires two cylindrical seats facing each other on the outer ring and inner ring.

Document DE102009023041 describes a wheel bearing comprising an outer ring and at least one inner ring, which are guided relative to one another around an axis of revolution of the wheel bearing, the wheel bearing further comprising a sealing device, the sealing device comprising at least one outer structure attached to the outer ring and an inner structure attached to the inner ring, the outer structure and the inner structure together delimiting a chicane passage having an inlet. The outer structure features a shrink-fitting portion shrunk onto the outer ring, and forms an annular gutter open radially outwards. The inlet of the chicane passage and the shrink-fitting portion of the outer structure are situated axially on either side of the gutter, the chicane passage and the gutter being situated on the same first side of a reference plane of the outer ring, perpendicular to the axis of revolution and tangent to an end wall of the outer ring. The shrink-fitting portion of the outer structure and the outer ring are situated on a second side of the outer ring reference plane, opposite the first side. The gutter has a side wall that bears entirely against the transverse end face of the outer ring, and the depth of the gutter is limited by the presence of the inner structure. The inner structure also supports an encoder that can be read radially across the bottom of the gutter by a sensor positioned in the gutter.

DISCLOSURE OF THE INVENTION

The aim of the invention is to remedy the disadvantages of the prior art and to offer a wheel bearing which reconciles a large pitch diameter and a satisfactory sealing function from the perspective of technical performance and financial cost.

According to a first aspect of the invention, a wheel bearing is proposed which comprises at least one outer ring and at least one inner ring, which are guided relative to one another around an axis of revolution of the wheel bearing, the wheel bearing further comprising a sealing device, the sealing device comprising at least one outer structure attached to the outer ring and an inner structure attached to the inner ring, the outer structure and the inner structure together delimiting a chicane passage having an inlet, the outer structure having a shrink-fitting portion shrunk onto the outer ring, the inner structure (78) having a shrink-fitting portion shrunk onto a shrink-fit surface of the inner ring. The outer structure forms an annular gutter open radially outwards, the inlet of the chicane passage and the shrink-fitting portion of the outer structure being situated axially on either side of the gutter, the chicane passage and the gutter being situated on a same first side of a reference plane of the outer ring, perpendicular to the axis of revolution and tangent to an end wall of the outer ring, the shrink-fitting portion of the outer structure and the outer ring being situated on a second side of the outer ring reference plane, opposite the first side. The gutter has a bottom and side walls situated axially on either side of the bottom, the side walls being further from the axis of revolution than the bottom.

Positioning the functional portion of the sealing device's outer structure axially outside the reference plane enables the sealing device to incorporate a gutter and a chicane passage, which together provide the bearing with excellent protection of against sprayed materials. The gutter allows liquid to drain away, minimizing exposure at the inlet of the chicane passage. Positioning the inlet of the chicane passage on the side of the gutter opposite the shrink-fitting portion is also particularly advantageous when the space available between the outer ring and inner ring is reduced, for example when the inner ring's raceway is close to the outer ring's reference plane.

The inner structure comprises a flat annular flange projecting radially from the shrink-fitting portion of the inner structure towards the outer ring, positioned opposite and at a short distance from one of the side walls of the gutter. Such a flange allows grease to be confined within the volume defined between the outer ring and my inner ring, enabling a seal lip to be eliminated (or its contact pressure reduced) if necessary, thus contributing to a reduction in friction torque. It can also be used to support an encoder, which is then positioned to be read by a sensor housed partly in the gutter.

A second aspect of the invention relates to a plain or rolling bearing 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 an axis of revolution of the bearing.

The inner ring has:at least one annular guideway,an axial end face facing in a reference axial direction parallel to the axis of revolution, the axial end face of the inner ring being tangent to an inner ring reference plane perpendicular to the axis of revolution and situated axially at a distance from the inner ring guideway in the reference direction,an axially extending shrink-fit surface between the axial end face of the inner ring and the guideway of the inner ring.

The outer ring has:at least one annular guideway opposite the inner ring guideway,an axial end face facing in the axial reference direction, the axial end face of the outer ring being tangent to a reference plane of the outer ring, perpendicular to the axis of revolution and situated axially at a distance from the guideway of the outer ring in the reference direction,an axially extending shrink-fit surface between the axial end face of the outer ring and the guideway of the outer ring.

The bearing further comprises a sealing device, the sealing device comprising at least:an outer structure integral with the outer ring, the outer structure comprising at least one shrink-fitting portion shrunk onto the shrink-fit surface of the outer ring and at least one functional portion situated on one side of the reference plane of the outer ring opposite the shrink-fitting portion of the outer structure, andan inner structure integral with the inner ring, the inner structure comprising at least one shrink-fitting portion shrunk onto the shrink-fit surface of the inner ring and at least one functional portion situated on one side of the reference plane of the inner ring opposite the shrink-fitting portion of the inner structure.

According to this second aspect of the invention, the functional portion of the outer structure integral with the outer ring forms a gutter open radially outwards, with at least part of the gutter axially overlapping at least part of the inner ring's shrink-fit surface. Positioning a gutter at least partially in the space between the inner ring reference plane and the outer ring reference plane prevents the gutter from having a negative impact on the bearing's axial dimensions.

The outer structure and the inner structure can preferably together delimit a chicane passage having an inlet, the inlet of the chicane passage and the shrink-fitting portion of the outer structure preferably being situated axially on either side of the gutter, the chicane passage and the gutter preferably being situated on the same first side of the reference plane of the outer ring, the shrink-fitting portion of the outer structure and the outer ring preferably being situated on a second side of the reference plane of the outer ring, opposite the first side.

Alternatively, and similarly to the first aspect of the invention, the inner structure may comprise a flat annular flange projecting radially from the shrink-fitting portion of the inner structure towards the outer ring, positioned opposite and at a short distance from one of the side walls of the gutter. Such a flange allows grease to be confined within the volume defined between the outer ring and my inner ring, enabling a seal lip to be eliminated (or its contact pressure reduced) if necessary, thus contributing to a reduction in friction torque. It can also be used to support an encoder, which is then positioned to be read by a sensor housed partly in the gutter.

The bearing according to this second aspect of the invention can be a rolling bearing, and in particular constitute a wheel bearing. The invention also relates to a motor vehicle wheel support device, comprising a bearing according to the second aspect of the invention, the inner ring being a rotating ring, preferably a wheel hub or a ring integral with a wheel hub, and the outer ring is a fixed ring having an interface for attachment to a wheel support, in particular a wheel pivot.

Naturally, various embodiments, discussed below, can be envisaged, which apply both to the wheel bearing according to the first aspect of the invention and, where applicable, to the plain or rolling bearing according to the second aspect of the invention.

In one embodiment, the chicane passage is delimited by a chicane wall of the outer structure and a chicane wall of the inner structure. Preferably, the chicane wall of the outer structure is situated axially between the reference plane of the outer ring and the chicane wall of the inner structure.

In one embodiment, the gutter is situated axially between the shrink-fitting portion of the outer structure and the chicane wall of the inner structure. The space surrounded by the gutter and situated between the gutter and the axis of revolution is not occupied by the chicane wall of the outer structure and is free to accommodate other components of the wheel bearing, for example part of the inner ring, and in particular a shrink-fit surface of the inner ring on which a shrink-fitting portion of the inner structure is shrunk.

In one embodiment, the chicane wall of the outer structure forms several additional gutters, situated inside the chicane passage. Assuming the outer ring is fixed, the gutters limit the penetration of pollutants into the chicane passage, and guide any pollutants that may still have entered by gravity back to the chicane passage inlet.

In one embodiment, the chicane wall of the inner structure forms several frustoconical walls facing the axis of revolution, each converging towards an apex further from the reference plane than the inlet. When the inner ring is a rotating ring intended to rotate with the wheel hub, such an arrangement enables any pollutants that may have penetrated inside the chicane passage to be centrifuged away, guiding them towards the inlet of the chicane passage. Ideally, the gutters in the chicane wall of the outer structure are combined with the truncated cone walls of the inner chicane wall, for optimum pollutant removal.

In one embodiment, the chicane wall of the outer structure forms several annular ribs of the outer structure, while the chicane wall of the inner structure forms several annular ribs of the inner structure, which are interposed in interspaces between the annular ribs of the outer structure.

In one embodiment, the inlet portion of the chicane wall of the inner structure is cylindrical, or frustoconical, converging towards an apex further from the reference plane than the inlet. In one embodiment, the inlet portion of the chicane wall of the outer structure is cylindrical, or frustoconical, converging towards an apex further from the reference plane than the inlet;

In one embodiment, the inlet of the chicane passage faces axially towards the gutter, and more generally towards the outer ring, which acts as a screen against splashing.

The bottom of the gutter is preferably closer to the axis of revolution than the inlet of the chicane passage. The inlet of the chicane passage preferably opens onto a radially outer perimeter of one of the gutter's side walls.

In one embodiment, the outer ring forms at least one raceway, the inner ring forming at least one raceway situated opposite the outer ring raceway and, together with the outer ring raceway, delimiting an inner volume of the wheel bearing open onto a sealing volume delimited by the outer structure of the sealing device and by the inner structure of the sealing device, the wheel bearing comprising at least one row of rolling bodies able to roll on the outer ring raceway and the inner ring raceway so as to allow relative rotational movement between the inner ring and the outer ring about an axis of revolution. The inlet of the chicane passage is further from the axis of revolution than a pitch circle defined by the row of rolling elements.

In one embodiment, the sealing device further comprises a resiliently deformable seal lip. The seal lip is preferably attached to a first of the inner or outer structures and comes into sliding contact against a seal seat formed on a second of the inner or outer structures. The seal lip and seal seat are preferably situated in the sealing volume.

According to a particularly advantageous embodiment, several of the following conditions are fulfilled:the seal seat is closer to the axis of revolution than the inlet of the chicane passage;the joint seat is closer to the axis of revolution than the pitch circle defined by the row of rolling elements;the seal seat is closer to the axis of revolution than a raceway bottom of the inner ring raceway;the seal seat is closer to the axis of revolution than a shrink-fitting portion of the inner structure, shrunk onto a shrink-fit surface of the inner ring.

This limits the circumference of the seal seat, and hence the friction torque between seal lip and seal seat.

Preferably, the seal lip is situated on the first side of the outer ring reference plane.

In one embodiment, the shrink-fitting portion of the outer structure is shrunk onto a radially inward-facing shrink-fit surface of the outer ring, which is at least partially situated axially between the raceway of the outer ring and the reference plane. Alternatively, the shrink-fit surface of the outer ring can be turned radially outwards.

In one embodiment, the shrink-fit surface of the outer ring is further from the axis of revolution than the pitch circle of the row of rolling elements, and optionally further from the axis of revolution than a raceway bottom of the outer ring raceway.

In one embodiment, the outer structure comprises a rigid frame, for example made of metal, particularly sheet metal, or plastic, forming the shrink-fitting portion. The frame can then be designed to form the gutter. The frame can also be designed to form the chicane wall of the outer structure.

In one embodiment, the inner ring has an axial end face facing in the axial reference direction. The axial end face of the inner ring can protrude from the axial end face of the outer ring in the axial reference direction. In one embodiment, the gutter is situated axially on either side of a reference plane of the inner ring, perpendicular to the axis of revolution and tangent to the axial end face of the inner ring.

Preferably, several of the following arrangements are created:the outer ring has an interface for attachment to a strut,the inner ring forms a wheel hub or is provided with an interface for attachment to a wheel hub,the inner ring has an interface for supporting, securing or shrink-fitting onto a torque converter,the shrink-fitting portion is cylindrical,the outer ring is made of one piece, and/orthe outer ring has an additional raceway positioned opposite and at a distance from an additional raceway formed on the inner ring or on a wheel hub integral with the inner ring.

For greater clarity, identical or similar elements are identified by identical reference signs in all of the Figures.

DETAILED DESCRIPTION OF EMBODIMENTS

FIG.1shows a motor vehicle drive wheel assembly10, comprising a fixed subassembly12, intended to be secured to a suspension member of a motor vehicle (not shown) and defining an axis of rotation XX, a rotating subassembly14, capable of rotating about the axis of rotation XX inside the fixed subassembly12, and guiding rolling bodies16,18between the rotating subassembly14and the fixed subassembly12.

The fixed sub-assembly12is here constituted by a single-piece solid metal outer ring20on which are formed in this embodiment two coaxial outer raceways22,24defining the axis of revolution XX, one of the outer raceways22being intended to be positioned on an outer side of the vehicle, and the other24being intended to be positioned on an inner side of the vehicle, i.e. closer to a median longitudinal vertical plane of the vehicle. The outer ring further comprises at least one attachment clamp26extending radially outward, in which bores28are formed for attaching the attachment clamp26to a suspension member30, in this case a strut pivot, via attachment elements32.

The rotating sub-assembly14comprises a wheel hub34, which forms an inner ring on the outside of the vehicle, a second inner ring36on the inside of the vehicle and a torque converter38.

The wheel hub34is a solid single-piece metal part, which comprises a flange40for attaching a drive wheel rim and a brake disc. The flange40has a flat face42bearing the brake disc or wheel rim, and is provided with attachment bores44, allowing the insertion of attachment elements of the rim and/or of the brake disc. The wheel hub34has a first inner raceway46facing the first outer raceway22.

The torque converter38is a solid one-piece metal part, which has a solid protruding end portion50and a flared middle portion52delimiting a cavity54, acting as a constant-velocity joint. The protruding portion50of the torque converter38is splined and mounted free, fitted or shrunk in a splined tubular cavity56of the wheel hub34, forming a splined contact interface. Furthermore,FIG.1shows means for attaching the torque converter38and the wheel hub34, which for example implement a nut58screwed to a threaded end of the protruding portion50, and bearing against a shoulder of the wheel hub34. The inner bearing ring36on the inside of the vehicle is shrunk onto a cylindrical shrink-fit surface60of the wheel hub34and clamped in the axial direction between the wheel hub34and the torque converter38.

An inner raceway62is formed on the inner rolling bearing ring36opposite the outer raceway24on the inside of the vehicle. The rolling bodies16,18form, on the one hand, a first row of rolling bodies16that roll on the outer raceway22and the inner raceway46on the outside of the vehicle and, on the other hand, a second row of rolling bodies18that roll on the outer raceway24and the inner raceway62om the inside of the vehicle.

These two rows of rolling elements16,18and the raceways22,24,46,62are protected by two sealing devices, namely a sealing device64on the outside of the vehicle, positioned between the outer ring20and the wheel hub34, and a sealing device66on the inside of the vehicle, positioned between the outer ring20and the inner bearing ring36.

The components of the wheel bearing10described so far are generic, and can be presented in many variants. In particular, the inner raceway46can be formed on a bearing ring attached to the wheel hub34. The inner ring36on the inside of the vehicle can be secured to the wheel hub34by a snap ring and, if necessary, have no contact with the torque converter38. The torque converter38can be attached to the wheel hub34by any means. The bearing may comprise just one row of rolling elements16, which may be balls or rollers.

We'll now take a closer look at the sealing device66situated on the inside of the vehicle, shown in detail onFIG.2, which seals between the outer bearing ring20and the inner bearing ring36, and more specifically protects a volume V situated between the raceway24of the outer ring20and the raceway62of the inner ring36. In this region, the outer bearing ring20has a shrink-fit surface68, which is cylindrical here and faces the axis of revolution XX, and an end wall70, which defines a reference plane PE of the bearing outer ring20, perpendicular to the axis of revolution XX and tangent to the end face70. The shrink-fit surface68extends axially and circumferentially in an region of the outer ring20situated between the raceway24on the inside of the vehicle and the end face70. The shrink-fit surface68on the outer ring is further away from the axis of revolution XX than a pitch circle C of the row of rolling elements18, and, in this embodiment, further away from the axis of revolution XX than a raceway bottom FE of the raceway24of the outer ring20.

The inner bearing ring36also has a shrink-fit face72, which in this case is cylindrical and faces radially outwards, and an end wall74, which defines a reference plane PI of the inner bearing ring36, perpendicular to the axis of revolution XX and tangent to the end face74. The shrink-fit surface72extends axially and circumferentially in an region of the inner ring situated between the raceway62on the inside of the vehicle and the end face74. The end face74of the inner bearing ring and the end face70of the outer bearing ring are rotated in a common direction D parallel to the reference axis XX, which will be an axial reference direction for the remainder of the presentation. In this embodiment, it may be noted that the reference plane PI of the inner bearing ring36is situated at a distance from the reference plane PE of the outer bearing ring20and offset in the axial reference direction D, so that the inner bearing ring36protrudes from the outer bearing ring20in the axial reference direction D, and passes through the reference plane PE of the outer bearing ring20. More specifically, at least part of the shrink-fit surface72of the inner bearing ring36is situated on one side of the reference plane PE of the outer bearing ring20opposite the shrink-fit surface68of the outer bearing ring20.

The sealing device66comprises an outer structure76integral with the outer ring20, and an inner structure78integral with the inner ring36.

The outer structure76comprises a shrink-fitting portion80shrunk onto the shrink-fit surface68of the outer ring20, and a functional portion forming a gutter82open radially outwards, a chicane wall84and, in this embodiment, two sealing lips86. The gutter82has a bottom822and side walls824, which are situated axially on either side of the bottom and are further from the axis of revolution than the bottom. In this embodiment, the outer structure76comprises a rigid frame762, for example made of sheet metal or plastic, and an overmold764. The frame762forms the shrink-fitting portion80and gutter82, while the overmolding764forms the chicane wall84and seal lips86.

The inner structure78comprises a shrink-fitting portion88shrunk onto the shrink-fit bearing surface72of the inner ring36, and a functional portion forming a seal seat90and a chicane wall92situated opposite the chicane wall84of the outer structure76to delimit a chicane passage S between the inner structure78and the outer structure76. The seal lips86are resiliently deformable and bear on the seal seat90, which is cylindrical in this embodiment. The inner structure78and the outer structure76of the sealing device together delimit an annular housing L for the seal seat90and the seal lips86, wherein the chicane passage S opens and which communicates with the internal volume V delimited by the raceway24of the outer bearing ring20and by the raceway62of the inner bearing ring36.

The shrink-fitting portion88and the functional portion of the inner structure78lie on either side of the reference plane PI of the inner ring36. This makes it possible to position the seal seat90closer to the axis of revolution XX than the shrink-fitting portion88. This arrangement is designed to minimize the diameter of the seal seat90, thereby minimizing the frictional torque between the seal lips86and seal seat90, and reducing the heat generated by this friction.

The chicane passage S has an inlet E delimited by an inlet portion of the chicane wall84of the outer structure76and by an inlet portion of the chicane wall92of the inner structure78. The inlet E of the chicane passage S and the shrink-fitting portion80of the outer structure76are situated axially on either side of the gutter82. The chicane passage S and the gutter82are situated on the same side of the reference plane PE of the outer ring20, opposite the side of the reference plane PE on which the shrink-fitting portion80of the outer structure76is situated. The inlet of the chicane passage is further from the axis of revolution XX than the seal seat90.

The chicane wall84of the outer structure76is formed by annular ribs94which project axially towards the chicane wall92of the inner structure78. Similarly, the chicane wall92of the inner structure78is formed by several annular ribs96, which project axially towards the chicane wall84of the outer structure76and are interposed in interspaces between the annular ribs94of the outer structure76. The annular ribs94of the outer structure76form several additional gutters98situated inside the chicane passage S. At the annular ribs96of the inner structure78, the chicane wall92has frustoconical facets922facing the axis of revolution and frustoconical walls924facing radially outwards.

The inlet E of the chicane passage S is annular and faces in an axial direction opposite the reference axial direction D, towards the outer bearing ring20. The inlet E is further from the axis of revolution XX than the bottom822of the gutter82. In this case, the inlet E is preferably further from the axis of revolution XX than the pitch circle C defined by the row of rolling elements18.

The inlet portion of the chicane wall92of the inner structure78is preferably frustoconical as shown, so as to converge towards an apex further from the outer ring reference plane PE than the inlet E. Similarly, the inlet portion of the chicane wall84of the outer structure76is preferably frustoconical as shown in the figures, so as to converge towards an apex further from the outer ring reference plane PE than the inlet E.

In this embodiment, it can be seen that the gutter82at least partially overlaps axially with the shrink-fit surface72of the bearing inner ring36and with the shrink-fitting portion88of the inner structure78. The chicane wall84of the outer structure76is situated entirely on one side of the reference plane PI of the inner bearing ring36, and entirely on one side of the gutter82, so that the gutter82is situated axially between the shrink-fitting portion80of the outer structure76and the chicane wall84of the outer structure76.

Optionally, the functional portion of the inner structure78can also form a seat99or a support for a static seal102cooperating directly or indirectly with a flared median portion52of the torque converter38and/or an interface for attaching a protective sleeve104of the torque converter38.

The inner structure78of the sealing device66comprises a frame782, preferably metal, which forms the shrink-fitting portion72and may also form the seal seat90. Alternatively, the seal seat90can be formed on an annular part attached to the frame782, which may or may not be made of a non-metallic material. Preferably, the inner structure78also comprises a second part784attached to a connection portion785of the frame782by any suitable means, in particular by gluing, overmolding or mechanical fastening, for example by shrinking or by fastening elements, or, as shown inFIGS.1,2and3, by resilient hooking. The connecting portion785of frame782here projects axially from seal seat90in reference direction D. The second part784may be made of plastic. It acts as a deflector, forming the chicane wall92of the inner structure and, where appropriate, the seat99or the support for static seal102, or even the static seal102itself. In the embodiment shown inFIGS.1and2, a third part786, together with the second part784, defines an additional gutter106close to the seal seat90.

In a variant not shown, the part forming the deflector can also form the seal seat.

In the embodiment shown inFIGS.1and2, the inner structure78also supports a preferably annular encoder108, positioned opposite a side wall824or the bottom822of the gutter82, and which may in particular be a multipolar magnetic encoder or a phonic wheel. With a sensor110penetrating locally into the gutter82, data, in particular position data, encoded on the encoder108can be read remotely through the wall824of the gutter82. The reading can be radial if the encoder108is positioned on the shrink-fitting portion88of the inner structure78, and if the shrink-fit is controlled so as not to induce uncontrolled deformation of the encoder108. Alternatively, and preferably, reading is axial, as shown inFIGS.1and2, in which case the encoder108is supported by a flat annular flange112projecting radially from the shrink-fitting portion88towards the outer bearing ring20. It should be noted that even in the absence of an encoder108, the flat annular flange112, positioned opposite and at a short distance from the side wall824, can be advantageous, in that it enables grease to be confined within the volume V, allowing, if necessary, one of the seal lips86to be eliminated and thus contributing to a reduction in friction torque.

FIG.3shows a variant of the sealing device66which differs from the embodiment shown inFIGS.1and2in that no encoder is used.

FIG.4shows a further variant, which differs from the embodiment shown inFIGS.1and2in the shape of the seal, which has only one seal lip86.

FIG.5shows another variant, which differs from the embodiment shown inFIGS.1and2in that the frame762of the outer structure76of the sealing device consists of two parts7621,7622fastened together by any suitable means, in this case by shrink-fitting and mechanical interlocking.

FIG.6shows another variant, without seal lip or seat. In this variant, the inner structure78of the sealing device66is shrunk onto a cylindrical bearing surface72formed on an extension362of the outer ring36.

FIG.7shows another variant, which differs from the previous one in that the outer structure76of the sealing device66is shrunk onto a preferably cylindrical surface168of the outer ring, which faces radially outwards.

In a variant not shown, the seal seat can have a flat annular face parallel to the reference plane of the inner ring, the outer structure of the sealing device then comprising a seal lip bearing axially against this flat face.

In a variant not shown, the outer ring's shrink-fit surface68is further away from the axis of revolution XX than the pitch circle C of the row of rolling elements18, and closer to the axis of revolution XX than a raceway bottom FE of the raceway24of the outer ring20.

The examples shown in the figures and discussed above are provided for illustrative purposes only. It is explicitly provided that it is possible to combine the various illustrated embodiments in order to provide others.

It is emphasized that all the features, as they become apparent to a person skilled in the art from the present description, drawings and attached claims, even if in concrete terms they have only been described in connection with other specific features, both individually and in any combinations, may be combined with other features or groups of features disclosed herein, provided that this has not been expressly excluded or that technical circumstances render such combinations impossible or meaningless.