FR3064705A1 - BEARING BEARING - Google Patents

Abstract

The invention relates to a rolling bearing comprising two members (1, 2) and rolling bodies (5) arranged in a space (6) formed between said members to allow their relative rotation about an axis, a side of the space (6) having an annular opening (8) equipped with a sealing system comprising a first device (12) integral with a first member (1) and a second device (13) integral with the second member (2), and a first (12a) and a second (13a) central wall respectively belonging to the first (12) and second (13) devices, each of the central walls (12a, 13a) extending into the opening (8) so that the first (12a) - respectively second (13a) - central wall forms with a central sector (13b, 12b) of the second (13) - respectively first (12) - device a reduced clearance of sealing, the central walls (12a, 13a) each extending in a conical geometry forming with the axis rotating an angle (αc) between 40 ° and 50 ° for the first central wall (12a) and an angle (βc) between 5 ° and 45 ° for the second central wall (13a).

Description

® FRENCH REPUBLIC

NATIONAL INSTITUTE OF INDUSTRIAL PROPERTY © Publication number: 3,064,705 (to be used only for reproduction orders)

©) National registration number: 17 52742

COURBEVOIE © Int Cl ⁸ : F16 C 19/36 (2017.01), F16C 33/76

A1 PATENT APPLICATION

©) Date of filing: 03.31.17. © Applicant (s): NTN-SNR ROULEMENTS - FR. (30) Priority: @ Inventor (s): FAUGERAS GILLES, MOTOT JEAN- CHRISTMAS and POURROY-SOLARI VINCENT. (43) Date of public availability of the request: 05.10.18 Bulletin 18/40. ©) List of documents cited in the report preliminary research: Refer to end of present booklet (© References to other national documents ® Holder (s): NTN-SNR ROULEMENTS. related: ©) Extension request (s): (© Agent (s): STRATO-IP Limited liability company.

£> 4 / ROLLING BEARING.

FR 3 064 705 - A1

The invention relates to a rolling bearing comprising two members (1,2) and rolling bodies (5) arranged in a space (6) formed between said members to allow their relative rotation about an axis, one side of the space (6) having an annular opening (8) equipped with a sealing system comprising a first device (12) secured to a first member (1) and a second device (13) secured to the second member (2), as well as a first (12a) and a second (13a) central walls belonging respectively to the first (12) and to the second (13) devices, each of the central walls (12a, 13a) extending in the opening (8) so that the first (12a) - respectively second (13a) - central wall forms with a central sector (13b, 12b) of the second (13) - respectively first (12) - device a reduced sealing game, the central walls (12a, 13a) each extending in a conical geometry, forming with the axis of rotation an angle (a _c ) between 40 ° and 50 ° for the first central wall (12a) and an angle (β ₀ ) between 5 ° and 45 ° for the second central wall (13a).

Φη

The invention relates to a rolling bearing comprising two members, interior and exterior respectively, as well as rolling bodies arranged in a bearing space formed between said members to allow their relative rotation about an axis.

In particular, the invention applies to rolling bearings of a motor vehicle, in particular to wheel bearings. Advantageously, a bearing according to the invention allows the mounting of a driving or non-driving wheel of a motor vehicle, the internal member being rotating and comprising means for fixing the wheel while the external member is fixed and comprises fixing means on a suspension element of the vehicle.

Particularly known are rolling bearings of the tapered type, in which the inner and outer members are each provided with at least one rolling track forming between said members a raceway in which is arranged a row of tapered rollers. More specifically, each of the rolling tracks has a frustoconical geometry extending between an outer edge and an inner edge of smaller diameter, the tapered rollers being in abutment on said tracks through their frustoconical periphery.

Indeed, this type of bearing, due to its ability to withstand significant radial and axial forces, finds its application particularly for the guiding in rotation of a motor vehicle wheel.

According to a so-called "inverted conical" embodiment, the outer member has a collar formed on the outer edge of the outer track by extending radially opposite the lateral faces of the rollers. In particular, especially when such a bearing is subjected to axial loads, the collar makes it possible to guarantee the cohesion of said bearing.

Rolling bearings are also known, in which the rolling bodies are in the form of balls, the internal and external members each being provided with at least one raceway forming a raceway in which a row of balls is arranged.

To prevent on the one hand the leakage of lubricant present in the bearing space and on the other hand the contamination of said space with external pollutants, at least one side of the bearing space has an annular opening which is equipped with a sealing system comprising a first device secured to a first member and a second device secured to the second member.

In particular, the sealing system may comprise an armature integral with a first member and a wall integral with the second member, said armature being equipped with a dynamic sealing element which has at least one lip disposed in frictional contact on a inner reach of the wall.

To meet the increasingly stringent specifications relating to tightness, in particular for the validation of wheel bearings by car manufacturers, this solution leads to a high friction torque which, in addition to the negative impact on energy necessary for the rotation of the bearing, causes a high operating temperature level and therefore premature wear of the rubbing lip. In addition, this wear is all the more rapid as pollutants can return to the level of the friction surface and remain there during rotation.

In an attempt to resolve this problem, it is possible to propose adding deflectors to form a baffle for entry into the rolling space, thereby limiting exchanges between said space and the outside, in particular at the level of the friction surface.

However, to obtain good sealing performance, these solutions require a complex set of parts to be added in order to be able to genuinely limit the friction torque of the sealing lips.

The invention aims to perfect the prior art by proposing a rolling bearing, in particular of the “inverted conical” or “ball” type, which is equipped with a system whose sealing performance is optimized while limiting the torque. of induced friction.

To this end, the invention provides a rolling bearing comprising two members and rolling bodies arranged in a bearing space formed between said members to allow their relative rotation about an axis, at least one side of the bearing space. having an annular opening which is equipped with a sealing system comprising a first device secured to a first member and a second device secured to the second member, said sealing system comprising at least first and second central walls belonging respectively at the first and at the second devices, each of the central walls extending in the opening so that the first - respectively second - central wall forms with a central sector of the second - respectively first - device a reduced sealing clearance, the walls units each extending along a conical geometry, forming with the axis d e rotation an angle between 40 ° and 50 ° for the first central wall and an angle between 5 ° and 45 ° for the second central wall.

Other objects and advantages of the invention will appear in the description which follows, given with reference to the appended FIGS. 1 to 4 which partially represent and in longitudinal section a rolling bearing equipped with a sealing system according to respectively a mode of realization of the invention.

In relation to these figures, a rolling bearing is described below, in particular for mounting a driving or non-driving wheel of a motor vehicle.

In this description, the terms "exterior" and "interior" are defined with respect to the axis of rotation of the bearing, respectively for a location distant and close to said axis. The terms "axial" and "radial" are also defined with respect to this axis, respectively for a direction along this axis and moving away from or approaching it. Furthermore, the terms “external” and “internal” are taken with reference to the representation of the bearing, respectively on the left and on the right in FIGS. 1 to 4.

The bearing comprises two members, namely in the figures a first member 1 disposed externally while being stationary and a second member 2 disposed internally while rotating. In the application considered, the wheel is intended to be associated with the internal member 2 and the external member 1 may have means for fixing the bearing to a suspension element of the motor vehicle, in particular in the form of a flange 3 with orifices 4 for receiving screws or rivets for fixing to such an element, as shown in FIGS. 2, 3 and 4.

The bearing comprises rolling bodies 5 arranged in a rolling space 6 formed between the members 1, 2, to allow their relative rotation about an axis. In particular, the rolling bodies 5 can be maintained in the rolling space 6 by means of a retention cage 7, as shown in FIGS. 2 to 4.

According to one embodiment, each member 1, 2 can have two axially spaced tracks, so as to form in the bearing space 6 two raceways in which are respectively arranged a row of rolling bodies 5, said rolling bodies being held in their respective rows via a retention cage 7.

At least one side of the rolling space 6 has an annular opening 8, through which said rolling space opens to the outside. In relation to the figures, the external member 1 has an axial ring 9 which is arranged axially facing a substantially radial surface 10 of the internal member 2, the annular opening 8 extending at the interface between said crown and said surface. In particular, the crown 9 is in the form of a ring of generally rectangular section which extends axially in the direction of the surface 10.

In FIG. 1, the rolling bodies 5 are in the form of balls. In FIGS. 2 to 4, the members 1, 2 are each provided with at least one annular track 1a, 2a for rolling forming between said members a raceway in which is disposed a row of tapered rollers 5, said track having a tapered geometry extending between an outer edge and an inner edge and on which the tapered rollers 5 are supported by means of their tapered periphery.

Furthermore, the internal edge of each rolling track 1a, 2a has a diameter which is less than the diameter of its external edge. Thus, advantageously, the bearings shown in Figures 2 to 4, by their ability to withstand significant radial and axial forces, find their application particularly for the guiding in rotation of a motor vehicle wheel.

The bearings in FIGS. 2 to 4 are of the “inverted conical” type, in that the external member 1 has a collar 11 formed on the external edge of the external track 1a by extending radially opposite the lateral faces 5a of the rollers 5.

In particular, the collar 11 is in the form of an annular shoulder which is produced on the external side of the external member 1, in particular on the free end of the axial crown 9.

The collar 11 has a radial bearing surface 11a on which the conical rollers 5 are supported by means of a lateral face 5a, said radial bearing extending between an outer edge and an inner edge having a frustoconical geometry, said edges being annular and the diameter of said outer edge being greater than the diameter of said inner edge.

To prevent on the one hand the leakage of lubricant present in the bearing space 6 and on the other hand the contamination of said space with external pollutants, in particular based on sludge, the annular opening 8 is equipped with a system of sealing.

The sealing system comprises a first device 12 secured to the outer member 1 and a second device 13 secured to the inner member 2. In particular, the first device 12 is carried by the axial ring 9 and the second device 13 is carried by the radial surface 10.

The sealing system comprises at least a first 12a and a second 13a central walls belonging respectively to the first 12 and to the second 13 devices, each of the central walls 12a, 13a extending in the opening 8 so that the first 12a - respectively second 13a - central wall forms with a central sector 13b, 12b of the second 13 - respectively first 12 - device a reduced sealing game.

In the embodiments shown, the first central wall 12a, that is to say the central wall 12a associated with the external member 1 which is fixed, surrounds the second central wall 13a which is rotating. In particular, the central walls 12a, 13a each have a base by defining a diameter around the axis of rotation of the bearing, the diameter defined by the first central wall 12a being greater than the diameter defined by the second central wall 13a.

At least one central wall 12a, 13a, and in particular the two central walls 12a, 13a in each of the embodiments shown, has a free end which is arranged opposite the central sector 12b, 13b corresponding to form the reduced sealing clearance at least partially at their interface.

Advantageously, the reduced sets of seals are formed substantially axially on either side of the opening 8 so as to form an S-baffle between the central walls 12a, 13a, and thus limit the risk of lubricant leakage. and / or the entry of pollutants through said opening.

At least one sealing device 12, 13 has a frame 14, 15 associated with the corresponding member 1, 2, the central wall 12a, 13a of said device extending from said frame. To do this, the frame 14, 15 has an inner surface 14b, 15b extending substantially radially in the opening 8 and from which extends the central wall 12a, 13a.

Furthermore, the armature 14, 15 has an axial bearing 14a, 15a of association with the member 1,2, in particular on a complementary axial bearing 9a, 10a, provided for this purpose on the crown 9 or the surface 10, according to said organ. In particular, the axial dimension of the bearing surface 14a, 15a is less than half a diameter of the rolling bodies 5, in particular the diameter of the balls in FIG. 1 and the diameter 4> r of the large lateral face 5a of the rollers 5 in FIGS. 2 to 4, in order to limit the axial size of the sealing device 12, 13.

In FIGS. 1 to 3, each device 12, 13 comprises such a frame 14, 15, while in FIG. 4, only the first device 12, that is to say the device associated with the external member 1, is provided with it, the central wall 13a and / or the central sector 13b being formed on the internal member 2.

In particular, in the embodiment of Figure 4, the radial surface 10 has a protrusion 16 on which extends the central wall 13a of the second sealing device 13, as well as a groove 17 in which the sector is formed central 13b of said device, said protuberance and said groove being in particular formed by machining the surface 10 of the rotating member 2.

In Figures 1 and 3, the frame 15 of the second device 13 is made of a plastic material, for example by molding, and is arranged to be associated with the internal member 2 by deformation, the axial bearing 15a having an external edge 18 snap-fastening in a groove 19 provided for this purpose on the complementary axial surface 10a.

The frames 14, 15 can also be made of a metallic material, in particular by folding a stamped sheet, the axial bearing 14a, 15a being arranged to be fitted on the corresponding complementary axial bearing 9a, 10a, as shown in FIGS. 1 , 3, 4 (for the first frame 14) and in Figure 2 (for the two frames 14, 15).

In FIG. 1, the axial bearing surface 14a of the first frame 14 is fitted onto a complementary axial bearing surface 9a formed inside the opening 8. In FIGS. 2 to 4, the crown 9 has an axial bearing surface 9a formed on an outer side of the opening 8 and on which the axial bearing 14a of the first frame 14 is fitted, as well as a radial recess 20 extending at the entrance to said opening and in which the inner bearing 14b extends of said first frame.

In FIGS. 1 to 3, the second central wall 13a is formed in one piece with the frame 15, in particular at the level of a free end of said frame. In the case of an armature 15 made of plastic material (Figures 1 and 3), the central wall 13a can in particular be formed during the molding of said armature. In the case of a frame 15 of metallic material (FIG. 2), the central wall 13a can be formed by folding its free end, in particular during the forming operation by stamping the frame 15.

In FIGS. 1 to 4, the frame 14 of the first sealing device 12 is equipped with an added element 21, in particular by overmolding, said element having the central wall 12a. In particular, the element 21 can be made of flexible material, for example of elastomer, in particular based on butadiene nitrile copolymer (NBR), possibly mechanically reinforced with fillers such as carbon black, hydrogenated NBR (HNBR), fluoropolymer or polyacrylate.

In addition, when the device 12, 13 is equipped with a frame 14, 15, the central sector 12b, 13b can in particular extend over a span of said frame.

In FIGS. 2 and 3, the free end of the second central wall 13a is arranged axially facing an interior portion of the recess 20 not covered by the interior bearing 14b, said interior portion thus forming the first central sector 12b.

To improve the tightness of the system, in particular at the level of the baffle formed by the central walls 12a, 13a, said central walls each extend in a conical geometry by forming with the axis of rotation of the bearing an angle a _c between 40 ° and 50 ° for the first central wall 12a and an angle βο of between 5 ° and 45 ° for the second central wall 13a.

Thus, the central walls 12a, 13a form in the opening 8 annular grooves making it possible to retain the external pollutants, in order to prevent their penetration into the rolling space 6. Furthermore, the angle a _c of the first wall central 12a may be greater than the angle βο of the second central wall 13a, in order to ensure greater retention of external pollutants as far upstream as possible from the opening 8.

Such a central wall 13a makes it possible to expel from the opening 8 the external pollutants which are retained there, due to the centrifugal effect generated by the rotation of the member 2. Furthermore, in the embodiments shown, the conical shape of the first central wall 12a, which is arranged upstream of the rotary central wall 13a, allows the pollutants ejected by centrifugal effect from said rotary wall to flow easily out of the opening 8.

To limit the entry of external pollutants into the opening 8, at least one sealing device 12, 13 may have an external wall 12c, 13c at least partially surrounding the central wall 12a, 13a of said device, in particular by presenting a base defining around the axis of rotation of the bearing a diameter which is greater than the base diameter of the central wall 12a, 13a of said device.

In all the embodiments shown, the second device 13 is provided with such an outer wall 13c. Furthermore, in FIGS. 2 to 4, the first device 12 is also provided with such an external wall 12c, said external wall being in particular attached by molding onto the frame 14, and more particularly by being formed in one piece with element 21.

In Figures 1 to 4, the outer wall 13c surrounds the opening 8 by forming a deflector, in order to retain external pollutants thereon, and thus prevent their penetration upstream of said opening.

In Figures 1 to 3, the outer wall 13c is formed in one piece with the frame 15 carrying the second central wall 13a. In FIG. 4, the second device 13 has an armature 22, for example of metallic material, which specifically has the outer wall 13c, said armature having an axial bearing surface 22a of association by fitting onto a complementary axial bearing body 10b formed for this purpose on the rotating member 2, in particular in the upper part of the surface 10.

The outer wall 13c is arranged to form, with the axial bearing surfaces 15a, 22a, 10a, 10b of association of the frame 15, 22 with the member 2, a gutter for retaining external pollutants. In addition, the fact of providing such a deflector 13c on the rotating member 2 makes it possible to eject the external pollutants which are retained there, due to the centrifugal effect generated by the rotation of said member.

In FIG. 1, the external wall 13c has a first portion 23a extending radially from an internal edge of the axial bearing 15a of association with the member 2, as well as a second portion 23b extending axially from an edge upper of said first portion.

In Figures 2 to 4, the outer wall 13c extends from the frame 15, 22 in a conical geometry by forming with the axis of rotation of the bearing an angle β _θ which is between 5 ° and 45 °.

In FIG. 2, the frame 15 has an axial U-shaped geometry having an inner branch 15c fixed to the member 2 and an outer branch 15d from which extends the outer wall 13c forming a deflector, the angle γ between the branches 15c, 15d being non-zero, in particular being between 0.5 and 3 °, in order to improve the shape of the gutter, and thus the retention of external pollutants on the deflector 13c.

In addition, the outer wall 12c, 13c of a sealing device 12, 13 can extend into the opening 8 by forming a reduced sealing clearance with an outer sector 12d, 13d of the other sealing device. sealing 12, 13.

In FIG. 1, the first 23a and the second 23b portions of the outer wall 13c extend respectively in axial view of a radial bearing 25a of the crown 9 and axially in a groove 25b formed on said crown on an outer side of opening 8, the reduced sealing clearance being formed at L at the interfaces between said portions and respectively the bearing 25a and the groove 25b.

In FIGS. 2 to 4, the outer wall 12c of the first sealing device 12 has a free end which is arranged in axial view of a substantially radial inner surface 26 of the frame 15, 22, and on which the outdoor sector 13d. In particular, the free end has a substantially radial fold 27 of sufficiently long length to reduce the dimensions of the sealing clearance, and thus further prevent the penetration of external pollutants by said clearance.

Advantageously, the outer wall 12c is made at least partially flexible, in order to allow the axial plating of its radial fold 27 on the inner surface 26, under the effect of the pressure exerted by external pollutants on said outer wall. Thus, the sealing clearance can be obstructed, which makes it possible to prevent the penetration of external pollutants into the opening 8.

The outer wall 12c extends from the first frame 14 in a conical geometry, which not only makes it possible to limit the entry of external pollutants into the opening 8, but also to facilitate the flow outside said opening of the pollutants ejected by centrifugal effect from the rotating central wall 13a. In particular, the outer wall 12c forms with the axis of rotation of the bearing an angle a _e which is between 40 ° and 50 °, being in particular equal to the angle a _c of the central wall 12a of the first device 12.

To prevent the entry of external pollutants and / or the leakage of lubricant at the level of the rolling space 6, at least one sealing device 12, 13 has an internal frame 14, 29 associated with the member 1,2 corresponding, said frame being equipped with a dynamic sealing element 30 which has at least one lip 30a-30b arranged in rubbing contact on an internal sector 31 of the other sealing device 12, 13.

In the embodiments shown, the internal reinforcement 14, 29 is associated with the fixed sealing device 12. In FIG. 1, the fixed sealing device comprises a single reinforcement 14, the dynamic sealing element 30 being formed on said frame, in particular by coming integrally with the element 21 carrying the central wall 12a.

In FIGS. 2 to 4, the first device 12 comprises an inner frame 29 which is distinct from the first frame 14, in particular by being formed of a part which is separate from that forming said first frame, said inner frame having an inner bearing 29b extending substantially radially in the opening 8 and carrying the dynamic sealing element 30.

The internal frame 29 is made of a metallic material, in particular by folding a stamped sheet, and has an axial bearing 29a intended to be associated by fitting on a complementary axial bearing 9b formed on the crown 9, in particular along a diameter Φη which is inscribed in the central walls 12a, 13a, in particular by being smaller than the diameters defined by the bases of said central walls 12a, 13a.

The dynamic sealing element 30 is attached, in particular by overmolding, to the internal frame 29. In particular, the dynamic sealing element 30 can be made of flexible material, for example elastomer, in particular based on copolymer butadiene nitrile (NBR), possibly mechanically reinforced with fillers such as carbon black, hydrogenated NBR (HNBR), fluoropolymer or polyacrylate.

In the embodiments shown, the dynamic sealing element 30 has an external lip 30a which is in rubbing contact on a radial portion of the internal sector 31, in particular formed in the lower part of the surface 10, as well as an annex lip 30b which is in rubbing contact on a substantially axial portion of said interior sector.

In particular, the presence of the conical central walls 12a, 13a upstream of the dynamic sealing element 30 makes it possible to limit the number of lips 30a, 30b in friction contact in the bearing, and thus to reduce the friction torque of said bearing .

In FIGS. 2 to 4, the dynamic sealing element 30 has a third lip 30c which extends from the inner surface 29b and above the outer lip 30a without coming into rubbing contact against the member 2, said third lip having a conical geometry in order to form a deflector to limit the direct contact of external pollutants against said external lip, and thus limit the wear of said external lip.

To comply with the mounting constraints of the bearing, the dimensions of the outer lip 30a can be adapted. In particular, in the embodiments shown in Figures 2 to 4, the outer lip 30a is in rubbing contact on the inner sector 31 with a diameter Φί which is less than the outer diameter Φ ₉ of the cage 7 for retaining the rollers 5 and / or less than the _pitch diameter Φ _{Ρ of} said rollers in the rolling space 6.

Claims (23)

1. Rolling bearing comprising two members (1, 2) and rolling bodies (5) arranged in a bearing space (6) formed between said members to allow their relative rotation about an axis, at least one side of the rolling space (6) having an annular opening (8) which is equipped with a sealing system comprising a first device (12) secured to a first member (1) and a second device (13) secured to the second member (2), said sealing system comprising at least a first (12a) and a second (13a) central walls belonging respectively to the first (12) and to the second (13) devices, each of the central walls (12a, 13a) extending in the opening (8) so that the first (12a) - respectively second (13a) - central wall forms with a central sector (13b, 12b) of the second (13) - respectively first (12) - device a reduced seal clearance, said bearing being characterized in that e the central walls (12a, 13a) each extend in a conical geometry, forming with the axis of rotation an angle (a _c ) between 40 ° and 50 ° for the first central wall (12a) and an angle ( β ₀ ) between 5 ° and 45 ° for the second central wall (13a). 2. Rolling bearing according to claim 1, characterized in that at least one central wall (12a, 13a) has a free end which is arranged opposite the central sector (12b, 13b) to form the reduced sealing clearance at least partially at their interface. 3. Rolling bearing according to one of claims 1 or 2, characterized in that the reduced sealing clearances are formed substantially axially on either side of the opening (8) so as to form a baffle in S between the central walls (12a, 13a). 4. Rolling bearing according to any one of claims 1 to 3, characterized in that the first central wall (12a) surrounds the second central wall (13a). 5. Rolling bearing according to any one of claims 1 to 4, characterized in that at least one sealing device (12, 13) has a frame (14, 15) associated with the member (1,2 ) corresponding, the central wall (12a, 13a) of said device extending from said frame. 6. Rolling bearing according to claim 5, characterized in that the central wall (13a) is formed in one piece with the frame (15), in particular at a free end of said frame. 7. Rolling bearing according to claim 5, characterized in that the frame (14) is equipped with an element (21) attached, in particular by overmolding, said element having the central wall (12a). 8. Rolling bearing according to one of claims 5 to 7, characterized in that a central sector (12b, 13b) of at least one sealing device (12, 13) extends over the frame ( 14, 15). 9. Rolling bearing according to any one of claims 5 to 8, characterized in that the frame (14, 15) has an axial bearing (14a, 15a) of association with the member (1,2), the axial dimension of said bearing being less than half a diameter (4> r) of the rolling bodies (5). 10. Rolling bearing according to any one of claims 1 to 9, characterized in that at least one member (2) has a projection (16) on which extends a central wall (13a) of the sealing device (13) integral with said body. 11. Rolling bearing according to any one of claims 1 to 10, characterized in that at least one member (2) has a groove (17) in which is formed the central sector (13b) of the sealing device ( 13) integral with said body. 12. Rolling bearing according to any one of claims 1 to 11, characterized in that at least one sealing device (12, 13) has an outer wall (12c, 13c) at least partially surrounding the central wall ( 12a, 13a) of said device. 13. Rolling bearing according to claim 12, characterized in that the outer wall (12c, 13c) extends in a conical geometry by forming with the axis of rotation an angle (a _e , β _θ ) which is between 40 ° and 50 ° in the case where the outer wall (12c) belongs to the first sealing device (12) and between 5 ° and 45 ° in the case where the outer wall (13c) belongs to the second sealing device ( 13). 14. Rolling bearing according to claim 13, characterized in that the angle (go) of the outer wall (12c) of the first sealing device (12) is equal to the angle (a _c ) of the central wall (12a) of said first device. 15. Rolling bearing according to any one of claims 12 to 14, characterized in that the outer wall (12c, 13c) of a sealing device (12, 13) extends in the opening (8) by forming a reduced sealing clearance with an external sector (12d, 13d) of the other sealing device (12,13). 16. Rolling bearing according to any one of claims 12 to 15, characterized in that the outer wall (12c, 13c) of a sealing device (12, 13) surrounds the opening (8) forming a deflector. 17. Rolling bearing according to claim 16, characterized in that the outer wall (13c) forming a deflector extends from a frame (15) associated with a member (2), said frame having an axial U-shaped geometry having a branch inner (15c) fixed to the member (2) and an outer branch (15d) from which extends said outer wall, the angle (y) between said branches being non-zero, in particular being between 0.5 and 3 °. 18. Rolling bearing according to any one of claims 1 to 17, characterized in that at least one sealing device (12) has an internal frame (14, 29) associated with the corresponding member (1), said frame being equipped with a dynamic sealing element (30) which has at least one lip (30a, 30b) arranged in rubbing contact on an interior sector (31) of the other sealing device (13). 19. Rolling bearing according to claim 18, characterized in that the internal frame (29) is associated with the member (1) according to a diameter (Φη) which is inscribed in the central walls (12a, 13a). 20. Rolling bearing according to one of claims 18 or 19, characterized in that the dynamic sealing element (30) has an outer lip (30a) which is in friction contact with a diameter (Φί) which is smaller to the _pitch diameter (Φ _Ρ ) of the rolling bodies (5) in the rolling space (6). 21. Rolling bearing according to any one of claims 18 to 20, characterized in that the rolling bodies (5) are held in the rolling space (6) by means of a retention cage (7), l dynamic sealing element (30) having an outer lip (30a) which is in rubbing contact with a diameter (Φί) which is less than the outer diameter (Φ ₉ ) of said cage. 22. Rolling bearing according to any one of claims 1 to 21, characterized in that it comprises an external member (1) and an internal member (2) each provided with at least one annular track (1a, 2a ) of rolling forming between said members a raceway in which is disposed a row of tapered rollers (5), said track having a frustoconical geometry extending between an outer edge and an inner edge and on which the tapered rollers (5) are supported via their frustoconical periphery, the external member (1) having a collar (11) formed on the external edge of the external track (1a) extending radially opposite the lateral faces (5a ) rollers (5). 23. Rolling bearing according to any one of claims 1 to 22, characterized in that a member (1) has an axial ring (9) which is arranged axially facing a substantially radial surface (10) of the other member (2) to form the opening (8) at their interface, the sealing devices 5 (12, 13) being respectively carried by said crown and said surface. 1/4 30 12 30b