Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
  • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
  • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
  • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
  • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
  • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
  • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
  • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
  • F16C33/72—Sealings
  • F16C33/76—Sealings of ball or roller bearings
  • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
  • F16C33/7886—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted outside the gap between the inner and outer races, e.g. sealing rings mounted to an end face or outer surface of a race
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
  • B60B27/00—Hubs
  • B60B27/0073—Hubs characterised by sealing means
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
  • F16C33/72—Sealings
  • F16C33/74—Sealings of sliding-contact bearings
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
  • F16C33/72—Sealings
  • F16C33/76—Sealings of ball or roller bearings
  • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
  • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
  • F16C33/782—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region
  • F16C33/7823—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region of sealing lips
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
  • F16C33/72—Sealings
  • F16C33/76—Sealings of ball or roller bearings
  • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
  • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
  • F16C33/783—Details of the sealing or parts thereof, e.g. geometry, material of the mounting region
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
  • F16C33/72—Sealings
  • F16C33/76—Sealings of ball or roller bearings
  • F16C33/80—Labyrinth sealings
  • F16C33/805—Labyrinth sealings in addition to other sealings, e.g. dirt guards to protect sealings with sealing lips
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C17/00—Sliding-contact bearings for exclusively rotary movement
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C2326/00—Articles relating to transporting
  • F16C2326/01—Parts of vehicles in general
  • F16C2326/02—Wheel hubs or castors
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
  • F16C33/72—Sealings
  • F16C33/76—Sealings of ball or roller bearings
  • F16C33/768—Sealings of ball or roller bearings between relatively stationary parts, i.e. static seals
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
  • F16C41/007—Encoders, e.g. parts with a plurality of alternating magnetic poles

Definitions

• TITLE PLAIN OR ROLLING BEARING EQUIPPED WITH A SEALING DEVICE WITH A JOINT SEAT CLOSE TO THE REVOLUTION AXIS
• the invention relates to a plain or rolling bearing, and in particular, although not exclusively, to such a bearing constituting a motor vehicle wheel bearing, preferably a drive and steering wheel bearing.
• the seal generates friction between the seal lip and the seat, and this friction increases with the diameter, which has a negative impact on the resistive torque and on the operating temperature.
• a large diameter seal requires additional assembly precision and reduced manufacturing tolerances.
• the insertion of a cassette seal in the wheel bearing requires two cylindrical seats facing each other on the outer ring and the inner ring.
• Document US Pat. No. 9,377,055 B2 illustrates a wheel bearing equipped with a sealing device consisting of a conventional cassette seal protected by a labyrinth seal, comprising an outer structure integral with an outer ring of the bearing and positioned facing an internal structure secured to a ring inside the bearing, the two inner and outer structures being without contact with each other.
• a cassette seal in the wheel bearing requires two cylindrical seats facing each other on the outer ring and the inner ring.
• a wheel bearing is described, equipped with a sealing device comprising an outer structure integral with an outer ring of the bearing and an inner structure integral with an inner ring of the bearing, the outer structure and the inner structure together delimiting a sealing volume, the inner structure comprising a shrink-fit portion shrunk on the shrink-fit surface of the inner ring and at least one seal seat, the outer structure comprising at least one seal lip in sliding contact against the seal seat, to close off the sealing volume.
• the seal seat is flat and extends in the direction of the axis of revolution so as to cover part of the axial end face of the inner ring. In such a device, the seal and the seal seat are directly exposed to pollutants.
• the seal seat which rotates with the inner ring, centrifugates the pollutants and contributes to throwing them in the direction of the seal, which is not favorable.
• a wheel bearing is described, equipped with a sealing device comprising an outer structure fixed to an outer ring of the bearing and an inner structure fixed to the inner ring of the bearing. , the outer structure and the inner structure together delimiting a sealing volume open to an inner volume of the bearing.
• the inner structure comprises a shrink-fit portion shrink-fitted on a shrink-fit surface of the inner ring and at least one seal seat.
• the outer structure comprises at least one seal lip in sliding contact against the seal seat so as to close off the sealing volume.
• the seal seat comprises a cylindrical part facing radially outwards and which covers the shrink-fit portion, and a flat portion which extends from the cylindrical part in the direction opposite to the axis of revolution.
• the resulting structure has a large number of parts and its complex assembly. Moreover, it is not suitable for large wheel bearings. diameter, since the seal seat is located radially outside the shrink-fit surface of the inner structure.
• the invention aims to remedy the drawbacks of the state of the art and to propose a plain or rolling bearing which reconciles a large pitch diameter and a satisfactory sealing function from a point of technical performance and price. of returns.
• 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 capable of rotating the relative to the other around an axis of revolution of the bearing, the inner ring having a guide path, the outer ring having at least one guide path located opposite the guide path of the inner ring and delimiting with the inner ring guide path an interior volume of the bearing, the inner ring having an axial end face facing in an axial direction of reference parallel to the axis of revolution, the axial end face being located axially at a distance of the guide path of the inner ring in the reference direction, the inner ring having a shrink-fit surface located axially between the axial end face and the guide path of the ring e inner, the bearing comprising a sealing device, the sealing device comprising at least one outer structure secured to the outer ring and an inner structure secured to the inner ring, the outer structure and the inner structure together delimiting a volume d sealing open
• the seal seat is rotated radially opposite the axis of revolution of the bearing.
• the inner structure further comprises a connecting portion projecting axially relative to the seal seat in the reference direction, and a deflector, projecting radially from the connecting portion in a radial direction away from the axis of revolution .
• the deflector forms with the outer structure a chicane passage opening into the sealing volume, the chicane passage having an inlet farther from the axis of revolution than the seal seat, the seal seat and the seal lip being positioned in the sealing volume and interposed between the chicane passage and the interior volume of the bearing.
• the geometry of the chicane passage promotes centrifugation of pollutants likely to penetrate it.
• the seal seat is closer to the axis of revolution than a bottom of the guide path of the inner ring.
• the cylindrical shrink-fitting surface of the inner ring is rotated radially opposite the axis of revolution of the bearing.
• the internal structure comprises a reinforcement forming the hooping portion and the seal seat.
• the deflector is fixed to the frame by hooking, hooping, gluing, by fixing elements or any other means.
• the inner structure comprises a static sealing portion bearing against a static seal intended to be interposed between the inner structure and a part integral with the inner ring, in particular a transmission bowl or a protective bellows of a transmission bowl.
• the static seal protects the connection between the inner ring and the part on which it is mounted.
• the internal structure includes an encoder. The encoder makes it possible to code information, in particular of position, read by a sensor, which is preferably stationary with respect to the external structure.
• the guide path of the outer ring is a raceway
• the guide path of the inner ring is a raceway
• the bearing being a rolling bearing comprising at least one row of rolling bodies capable of rolling on the raceway of the outer ring and the raceway of the inner ring so as to allow relative rotational movement between the inner ring and the outer ring around the axis of revolution.
• the invention makes it possible to increase the pitch diameter of the bearing without negatively impacting the resistant torque of the bearing.
• the seal seat is closer to the axis of revolution than a pitch circle defined by the row of rolling elements. By thus reducing the circumference of the seal seat, the friction torque of the bearing is reduced.
• the latter relates to a motor vehicle wheel support device, characterized in that it comprises a bearing according to any one of the preceding claims, 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.
• Fig. 1 a view in axial section of a wheel support assembly comprising a wheel bearing according to a first embodiment of the invention
• Fig. 2 a detail view of certain components of the wheel bearing of FIG. 1;
• Fig. 3 a detail view of certain components of a wheel bearing according to a second embodiment of the invention
• Fig. 4 a detail view of certain components of a wheel bearing according to a third embodiment of the invention
• Fig. 5 a detail view of certain components of a wheel bearing according to a fourth embodiment of the invention.
• FIG. 1 a rolling bearing constituting a motor vehicle drive wheel assembly 10, comprising a fixed sub-assembly 12, intended to be secured to a suspension member of a motor vehicle (not shown) and defining an axis of revolution XX, a rotating sub-assembly 14, capable of rotating around the axis of revolution XX inside the fixed sub-assembly 12, and rolling guide bodies 16, 18 between the sub- rotating assembly 14 and the fixed sub-assembly 12.
• the fixed sub-assembly 12 is here constituted by a one-piece solid metal outer ring 20 on which are formed in this embodiment two outer raceways 22, 24 coaxial defining the axis of revolution XX, one of outer raceways 22 being intended to be positioned on an exterior side of the vehicle, and the other 24 being intended to be positioned on an interior side of the vehicle, i.e. closer to a vertical plane median longitudinal of the vehicle.
• the outer ring further comprises at least one fixing flange 26 extending radially outwards, in which bores 28 are formed for fixing the fixing flange 26 to a suspension member 30, in this case a pivot. suspension strut, by means of fixing elements 32.
• the rotating sub-assembly 14 comprises a wheel hub 34 which forms an inner bearing ring on the outside of the vehicle, a second inner bearing ring 36 located on the inside of the vehicle and a transmission bowl 38.
• the wheel hub 34 is a solid one-piece metal part, which includes a flange 40 for fixing a drive wheel rim and/or a brake disc.
• the flange 40 has a flat face 42 supporting the brake disc or the wheel rim, and is provided with fixing bores 44, allowing the insertion of fixing elements of the rim and/or of the brake.
• On the wheel hub 34 is formed a first inner raceway 46 facing the first outer raceway 22.
• the transmission bowl 38 is a solid one-piece metal part which, in this embodiment, has a solid end protruding portion 50 and a flared middle portion 52 delimiting a cavity 54 of constant velocity joint.
• the protruding portion 50 of the transmission bowl 38 is splined and mounted free, adjusted or shrunk in a splined tubular cavity 56 of the wheel hub 34, forming a splined contact interface.
• Figure 1 means for fixing the transmission bowl 38 and the wheel hub 34, which implement a nut 58 screwed to a threaded end of the projecting portion 50, and resting against a shoulder of the wheel hub 34.
• the inner bearing race 36 on the interior side of the vehicle is shrunk on a cylindrical shrunk surface 60 of the wheel hub 34 and pinched in the axial direction between the wheel hub 34 and the transmission bowl 38.
• An inner raceway 62 is formed on the inner raceway 36 facing the outer raceway 24 located on the inside of the vehicle.
• the rolling bodies 16, 18 form on the one hand a first row of rolling bodies 16 which roll on the outer raceway 22 and the inner raceway 46 on the exterior side of the vehicle, and on the other hand a second row of bodies rollers 18 which roll on the outer raceway 24 and the inner raceway 62 on the inside of the vehicle.
• sealing devices namely a sealing device 64 located on the outside of the vehicle, positioned between the outer ring 20 and the wheel hub 34, and a sealing device 66 located on the side inside the vehicle, positioned between the outer race 20 and the inner bearing race 36.
• the components of the wheel bearing 10 described so far are generic, and can occur in multiple variants.
• the inner raceway 46 be formed on a bearing ring attached to the wheel hub 34.
• the inner ring 36 on the inside of the vehicle can be fixed to the wheel hub 34 by a rivet and n if necessary, have no contact with the transmission bowl 38.
• the attachment between the transmission bowl 38 and the wheel hub 34 can be achieved by any means.
• the bearing may comprise only one row of rolling bodies 16, and these may consist of balls or rollers.
• the sealing device 66 located on the inside of the vehicle, illustrated in detail in Figure 2, and which seals between the outer bearing race 20 and the inner bearing race 36, and more specifically the protection of a volume V located between the raceway 24 of the outer race 20 and the raceway 62 of the inner race 36.
• the outer race race 20 has a bearing surface of hooping 68, which here is cylindrical and turned towards the axis of revolution XX, and an end wall 70, which makes it possible to define a reference plane PE of the outer bearing ring 20, perpendicular to the axis of revolution XX and tangent to the end face 70.
• the hooping surface 68 extends, in the axial direction and in the circumferential direction, in a zone of the outer ring 20 located between the raceway 24 located on the interior side of the vehicle and the face of end 70.
• the shrink-fit surface 68 of the outer race is further from the axis of revolution XX than a pitch circle C of the row of rolling bodies 18, and, in this embodiment, further from the axis of revolution XX than a bottom of the raceway FE of the raceway 24 of the outer ring 20.
• the inner bearing ring 36 also includes a shrink-fit surface 72, which here is cylindrical and turned radially outward, and an end wall 74, which makes it possible to define a reference plane PI of the inner ring. bearing 36, perpendicular to the axis of revolution XX and tangent to the end face 74.
• the hooping surface 72 extends, in the axial direction and in the circumferential direction, in a zone of the inner ring located between the raceway 62 located on the interior side of the vehicle and the end face 74.
• the face d end 74 of the inner bearing ring and the end face 70 of the outer bearing ring are turned in a common direction D parallel to the reference axis XX, which will be a reference axial direction for the rest of the 'exposed.
• the reference plane PI of the inner bearing race 36 is located at a distance from the reference plane PE of the outer bearing race 20 and offset in the axial direction of reference D, so that the inner bearing ring 36 projects relative to outer bearing ring 20 in the reference axial direction D, and crosses the reference plane PE of outer bearing ring 20. More specifically, at least part of the bearing surface 72 of the inner bearing race 36 is located on one side of the reference plane PE of the outer bearing race 20 opposite to the shrink-fit surface 68 of the outer bearing race 20.
• the sealing device 66 comprises an outer structure 76 secured to the outer ring 20, and an inner structure 78 secured to the inner ring 36.
• the outer structure 76 comprises a hooping portion 80 hooped on the hooping surface 68 of the outer ring 20, and a functional portion forming a gutter 82 open radially outwards, a baffle wall 84, and, in this embodiment, two seal lips 86.
• the gutter 82 comprises a bottom 822 and side walls 824, which are located axially on either side of the bottom and are farther from the axis of revolution than the bottom.
• the outer structure 76 comprises a rigid reinforcement 762, for example made of sheet metal or plastic, and an overmolding 764.
• the reinforcement 762 forms the hooping portion 80 and the gutter 82, while the overmolding 764 forms the baffle wall 84 and the seal lips 86.
• the inner structure 78 comprises a hooping portion 88 hooped on the hooping surface 72 of the inner ring 36, and a functional portion forming a seal seat 90 and a baffle wall 92 located opposite the baffle wall 84 of the outer structure 76 to delimit a chicane passage S between the inner structure 78 and the outer structure 76.
• the seal lips 86 are elastically deformable and bear on the seal seat 90 which, in this embodiment, is cylindrical .
• the inner structure 78 and the outer structure 76 of the sealing device together delimit an annular housing L for the seal seat 90 and the seal lips 86, housing into which opens the baffle passage S and in communication with the internal volume V delimited by the raceway 24 of the outer bearing race 20 and by the raceway 62 of the inner bearing race 36.
• the hooping portion 88 and the functional portion of the inner structure 78 are located on either side of the reference plane PI of the inner ring 36. It is thus possible to position the seal seat 90 at a higher close distance from the axis of revolution XX than the shrink-fit portion 88. This arrangement aims to minimize the diameter of the seal seat 90 and makes it possible to minimize the friction torque between the seal lips 86 and the seal seat 90, and to reduce the heat produced by this friction.
• the baffle passage S has an inlet E delimited by an inlet portion of the baffle wall 84 of the outer structure 76 and by an inlet portion of the baffle wall 92 of the inner structure 78. Entry E of the baffle passage S and the hooping portion 80 of the outer structure 76 are located axially on either side of the gutter 82.
• the baffle passage S and the gutter 82 are located on the same first side of the reference plane PE of the outer ring 20 opposite to the side of the reference plane PE where the hooping portion 80 of the outer structure 76 is located. the seal seat 90.
• the baffle wall 84 of the outer structure 76 is formed by annular ribs 94 which project axially toward the baffle wall 92 of the inner structure 78.
• the baffle wall 92 of the inner structure 78 is formed by one or more annular ribs 96, which protrude axially towards the baffle wall 84 of the external structure 76 and come to be interposed in the interspaces between the annular ribs 94 of the outer structure 76.
• the annular ribs 94 of the outer structure 76 form one or more additional gutters 98 located inside the baffle passage S.
• the baffle wall 92 comprises frustoconical facets 922 facing the axis of revolution and frustoconical walls 924 facing radially outwards.
• the entry E of the passage in baffle S is annular and turned in an axial direction opposite to the axial direction of reference D, towards the outer bearing ring 20.
• the entry E is farther from the axis of revolution XX than the bottom 822 of the gutter 82.
• the inlet E is preferably farther from the axis of revolution XX than the pitch circle C defined by the row of rolling elements 18.
• the inlet portion of the baffle wall 92 of the inner structure 78 is preferably tapered as shown, so as to converge towards a vertex farther from the reference plane of the outer ring PE than the inlet E.
• the inlet portion of the baffle wall 84 of the outer structure 76 is preferably tapered as shown in the figures, so as to converge towards a vertex farther from the reference plane PE of the outer ring than the entry E.
• the gutter 82 is located partially at least in axial overlap with the hooping surface 72 of the inner bearing ring 36 and with the hooping portion 88 of the inner structure 78.
• the wall baffle 84 of the outer structure 76 is located entirely on one side of the reference plane PI of the inner bearing race 36, and entirely on one side of the gutter 82, so that the gutter 82 is located axially between the hooping portion 80 of the outer structure 76 and the baffle wall 84 of the outer structure 76.
• the functional portion of the interior structure 78 can also form a seat 99 or a support for a static seal 102 cooperating directly or indirectly with the flared middle portion 52 of the transmission bowl 38 and/or a fixing interface of a protective sleeve 104 of the transmission bowl 38.
• the inner structure 78 of the sealing device 66 comprises an armature 782, preferably metallic, which forms the hooping portion 72 and can also form the seal seat 90.
• the seal seat 90 can be formed on an annular piece attached to the armature 782, this armature 782 possibly being made of a non-metallic material or not.
• the inner structure 78 further comprises a second part 784 fixed to a connection portion 785 of the reinforcement 782 by any appropriate means, in particular by gluing, overmolding or mechanical fixing, for example by shrink fitting or by fixing elements. , or, as illustrated in Figures 1 to 3, by elastic attachment.
• the connection portion 785 of the armature 782 here projects axially relative to the seal seat 90 in the reference direction D.
• the second part 784 can be made of plastic. It constitutes a deflector which forms the baffle wall 92 of the interior structure and, where applicable, the seat 99 or the support for the gasket 102, or even the gasket 102 itself.
• a third part 786 delimits with the second part 784 an additional gutter 106 near the seal seat 90.
• the part constituting the deflector can also form the seal seat.
• the inner structure 78 also serves as a support for an encoder 108, preferably annular, positioned opposite a side wall 824 or the bottom 822 of the gutter 82, and which can in particular be a multipolar magnetic encoder or a phonic wheel. It is thus possible, with a sensor 110 penetrating locally into the gutter 82, to read remotely through the wall 824 of the gutter 82 a datum, in particular a position datum, coded on the encoder 108. The reading can be radial if the encoder 108 is positioned on the hooping portion 88 of the internal structure 78, and if the hooping is controlled so as not to induce uncontrolled deformation of the encoder 108.
• an encoder 108 preferably annular, positioned opposite a side wall 824 or the bottom 822 of the gutter 82, and which can in particular be a multipolar magnetic encoder or a phonic wheel. It is thus possible, with a sensor 110 penetrating locally into the gutter 82, to
• the reading is axial, as illustrated in FIGS. 1 and 2, the encoder 108 then being supported by a flat annular flange 112 projecting radially from the hooping portion 88 towards the outer bearing race 20.
• the collar annular plane 112 positioned facing and at a short distance from the side wall 824, can be advantageous, in that it allows the fat to be confined inside the volume V, allowing, if necessary, to eliminate one of the seal lips 86 and thus contributing to a reduction in the friction torque.
• Figure 3 is illustrated a variant of the sealing device 66 which differs from the embodiment of Figures 1 and 2 by the absence of encoder.
• Figure 4 is illustrated another variant, which differs from the embodiment of Figures 1 and 2 by the shape of the seal, which has only one seal lip 86.
• Figure 5 is illustrated another variant, which differs from the embodiment of Figures 1 and 2 in that the armature 762 of the outer structure 76 of the sealing device consists of two parts 7621, 7622 fixed to each other by any appropriate means, here by hooping and mechanical attachment.
• the seal seat may comprise a flat annular face, parallel to the reference plane of the inner ring, the external structure of the sealing device then comprising a seal lip coming into axial bearing against this flat face.
• the sealing device described can be used in applications other than the protection of a wheel bearing, and will advantageously be applicable to any plain or rolling bearing, and in particular to any plain or rolling bearing whose outer ring is intended to be fixed and the inner ring is intended to rotate.
• the raceways 22, 24, 46, 62 will be referred to as guide paths.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Rolling Contact Bearings (AREA)
• Sealing Of Bearings (AREA)
• Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
• Sealing With Elastic Sealing Lips (AREA)

Priority Applications (4)

Applications Claiming Priority (2)

Publications (1)

Family

ID=74860264

Family Applications (1)

Country Status (6)

Cited By (1)

Citations (4)

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• 2021
  • 2021-01-29 FR FR2100908A patent/FR3119427B1/fr active Active
  • 2021-12-30 US US18/262,742 patent/US12338861B2/en active Active
  • 2021-12-30 EP EP21840645.2A patent/EP4204700B1/fr active Active
  • 2021-12-30 JP JP2023545949A patent/JP7837986B2/ja active Active
  • 2021-12-30 WO PCT/EP2021/087876 patent/WO2022161734A1/fr not_active Ceased
  • 2021-12-30 CN CN202180092459.7A patent/CN116802411A/zh active Pending

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