Bearing comprising an oil-conveying means

Abstract

The invention relates to a bearing (10) comprising a first bore intended to receive a rotational guide means (40) for a shaft (20), a second bore intended to be passed through by such a shaft (20), the first and second bores being coaxial or substantially coaxial with a main axis (AP) of the bearing (10), the bearing (10) comprising a shoulder extending radially from or substantially from the second bore, the shoulder comprising an outer surface, the shoulder comprising a means for conveying lubricating oil under pressure from the outer surface to the second bore.

Description

[0001] DESCRIPTION

[0002] TITLE: Bearing comprising an oil conveying means.

[0003] Technical field of the invention

[0004] The invention relates to a bearing comprising a means for conveying lubricating oil. The invention further relates to an arrangement comprising such a bearing and a shaft passing through such a bearing. The invention further relates to a vehicle comprising such an arrangement or such a bearing.

[0005] State of the prior art

[0006] A vehicle, in particular a motor vehicle, comprises a powertrain. Such a powertrain generally comprises at least one heat engine and / or at least one electric motor and at least one gearbox. Such a gearbox is generally arranged between the engine(s) and at least one transmission shaft intended to transmit torque to at least one means in contact with the ground such as a wheel. Such a gearbox generally comprises gears meshing with each other and uses oil for its lubrication. In particular, such a gearbox comprises at least one so-called "idler" or "idler-mounted" gear. Such a gear requires lubrication, in particular an oil supply, at its contact zone with a shaft on which it rotates or translates.

[0007] However, in the case of an element arranged outside such a gearbox at the end of such a shaft supporting at least one idler gear, it is complex to convey lubricating oil to such an idler-mounted gear.

[0008] Presentation of the invention

[0009] The aim of the invention is to provide a bearing which overcomes the above drawbacks. In particular, the invention proposes an arrangement allowing a simple architecture at the level of a bearing of a gearbox while ensuring optimal lubrication at the level of at least one idler gear.

[0010] Summary of the invention

[0011] To achieve this objective, the invention relates to a bearing comprising:

[0012] - a first bore intended to receive a rotational guide means for a shaft,

[0013] - a second bore intended to be traversed by such a shaft, the first and second bores being coaxial or substantially coaxial with a main axis of the bearing, the bearing comprising a shoulder extending radially from or substantially from the second bore, in particular coaxial with the main axis, the shoulder comprising an external surface, the shoulder comprising a conveying means for pressurized lubricating oil from the external surface to the second bore.

[0014] The oil delivery means may include:

[0015] - an external circumferential groove which may be provided in the external surface of the shoulder, the external circumferential groove being able to extend in a plane perpendicular to the main axis of the bearing,

[0016] - an internal circumferential groove which can be provided in the second bore, the internal circumferential groove being able to extend in the plane perpendicular to the main axis of the bearing,

[0017] - at least one main radial hole capable of extending between the outer circumferential groove and the inner circumferential groove.

[0018] The bearing may comprise a flange, in particular extending radially from the shoulder, and an oil inlet, in particular of the conduit type, for supplying the oil conveying means may pass through the flange. The invention also relates to an arrangement comprising:

[0019] - a shaft extending coaxially or substantially coaxially with the main axis of a bearing, the shaft comprising an axial hole, at least one main radial duct, and at least one secondary radial duct, the radial ducts opening into the axial hole,

[0020] - a bearing as defined previously, the second bore of the bearing being crossed by the shaft.

[0021] The arrangement may further include:

[0022] - a gear changing device comprising a casing and comprising at least one pinion mounted loosely on the shaft opposite the at least one secondary radial conduit, in particular a gear changing device of the gearbox or reducer type, the shaft being able to pass through the casing towards the outside of the gear changing device so as to be driven in rotation or to drive in rotation an element, in particular an electrical machine, arranged outside the gear changing device.

[0023] The arrangement may comprise a pump for delivering oil under pressure, in particular an electric pump, arranged within the gear changing device, the pump being able to be connected directly or indirectly to the oil conveying means.

[0024] The bearing can be fixed to the housing at an inner face of the housing.

[0025] The housing may include a centering bore and the bearing shoulder may be centered within this centering bore.

[0026] The housing may include a cavity opening into the centering bore and the inlet may open into the cavity so as to supply oil to the conveying means. The conveying means and the at least one main radial duct of the shaft may extend in the same plane or substantially in the same plane perpendicular to the main axis of the bearing to facilitate the passage of oil from the conveying means to the axial hole so as to supply oil to the at least one secondary radial duct.

[0027] The axial hole of the shaft may be provided from a first end of the shaft, the axial hole being able to be plugged at the first end, in particular by a plug.

[0028] The invention also relates to a vehicle, in particular a motor vehicle, comprising an arrangement as defined previously or a bearing as defined previously.

[0029] Presentation of figures

[0030] These objects, characteristics and advantages of the present invention will be explained in detail in the following description of an embodiment given without limitation in relation to the attached figures among which:

[0031] Figure 1 is a schematic view of a motor vehicle according to one embodiment of the invention.

[0032] Figure 2 is a perspective view of an arrangement according to one embodiment of the invention.

[0033] Figure 3 is an exploded perspective view of the arrangement according to the embodiment of the invention.

[0034] Figure 4 is a sectional view, along a plane passing through the main axis of a bearing, of the arrangement according to the embodiment of the invention.

[0035] Figure 5 is a perspective view of a housing of a gear changing device of the arrangement according to the embodiment of the invention.

[0036] Figure 6 is a partial sectional view of a shaft of the arrangement according to the embodiment of the invention. Figure 7 is a partial sectional view of the bearing according to the embodiment of the invention.

[0037] Detailed description

[0038] The direction in which a vehicle, especially a motor vehicle, moves in a straight line is defined as the longitudinal direction X. By convention, the direction perpendicular to the longitudinal direction, located in a plane parallel to the ground, is called the transverse direction Y. The third direction, perpendicular to the other two, is called the vertical direction Z. Thus, a direct XYZ reference frame is used in which X is the longitudinal direction in the front-rear direction of the vehicle, therefore directed backwards, Y is the transverse direction directed to the right and Z is the vertical direction directed upwards. The forward direction corresponds to the direction in which the vehicle usually moves in the longitudinal direction and is opposite to the rear direction.

[0039] As illustrated in Figure 1, a vehicle, preferably a motor vehicle 1, comprises an arrangement 5. The arrangement 5 or the vehicle 1 comprises a bearing 10.

[0040] As illustrated in Figures 2, 3 and 4, the arrangement 5 comprises a bearing 10. The bearing 10 comprises a main axis AP. The arrangement 5 further comprises a shaft 20. The shaft 20 extends coaxially, or substantially coaxially, with the main axis AP of the bearing 10.

[0041] More specifically, as illustrated in particular in Figures 4 and 7, the bearing 10 comprises a first bore 11. The first bore 11 is intended to receive a rotational guide means 40 for the shaft 20. For example, the rotational guide means is a ring obtained from a material having a low coefficient of friction. Alternatively, the rotational guide means is for example a ball bearing, or needle bearing or roller bearing. The bearing 10 further comprises a second bore 17. The first bore 11 and the second bore 17 are traversed by the shaft 20. The first and second bores 11, 17 are coaxial, or substantially coaxial, with, relative to, the main axis AP of the bearing 10. The bearing 10 further comprises a shoulder 12 extending radially from, or substantially from, the second bore 17. Preferably, the shoulder 12 is coaxial with the main axis AP. More preferably, the shoulder 12 is cylindrical.The shoulder 12 comprises an external surface 13, for example cylindrical.

[0042] As illustrated in FIG. 4 in particular, the shoulder 12 comprises a conveying means 30 for lubricating oil from the external surface 13 of the shoulder 12 to the second bore 17 of the bearing 10.

[0043] Preferably, as illustrated in Figure 7, the oil conveying means 30 comprises an external circumferential groove 14 formed in, or on, or at the external surface 13 of the shoulder 12. The external circumferential groove 14 extends in a plane A perpendicular to the main axis AP of the bearing 10 illustrated in Figure 4. The oil conveying means 30 further comprises an internal circumferential groove 15 formed in, or on, or at the second bore 17. The internal circumferential groove 15 then also extends in the plane A, or substantially in the plane A. Preferably, the circumferential grooves 14, 15 are centered relative to the plane A. The conveying means 30 further comprises at least one main radial hole 16 extending between the external circumferential groove 14 and the internal circumferential groove. 15. For example, the conveying means 30 comprises between two and twelve main radial holes 16.Preferably, six main radial holes 16 are provided distributed angularly every sixty degrees. For example, as illustrated in particular in Figures 4 and 7, the bearing 10 comprises a flange 18, or external radial edge, or external radial extension. Preferably, the flange 18 extends radially from the shoulder 12, at a plane B perpendicular to the main axis AP of the bearing 10. In other words, the planes A and B are parallel two by two and offset from each other in the direction of the main axis AP, that is to say that the planes A and B are not merged. Preferably, the bearing 10 also comprises an inlet 31 or tapping for lubricating oil. For example, as illustrated in Figures 2, 3, 4 and 7, the inlet 31 is of the conduit type, for example rigid, for example tubular of circular section, preferably bent.

[0044] Preferably, the inlet is of the pipe type intended to receive a flexible pipe. In this case, the inlet 31 preferably comprises a bulge or excess thickness 32 at its connection end to ensure sealing while ensuring that a flexible oil supply pipe inserted into the inlet 31 is held in position. The inlet 31 makes it possible to supply oil to the conveying means 30 by passing through the flange 18.

[0045] Alternatively, the intake 31 is flexible or includes a flexible portion.

[0046] More specifically, as illustrated in particular in FIG. 4, the shaft 20 comprises an axial hole 21. The shaft 20 further comprises at least one main radial duct 22 opening into the axial hole 21. For example, four main radial ducts 22, for example distributed every 90 degrees, are provided in the shaft 20. Alternatively, more main radial ducts 22 may be provided. The shaft 20 further comprises at least one secondary radial duct 23 opening into the axial hole 21. For example, two secondary radial ducts 23 pass right through the shaft 20, being centered or substantially centered on the axis of the shaft 20. In this case, the two secondary radial ducts 23 are arranged at 180 degrees from each other. Alternatively, more secondary radial ducts 23 may be provided.

[0047] Advantageously, as illustrated in Figure 4 in particular, the arrangement 5 also comprises a gear changing device 2. The gear changing device 2 is for example of the gearbox or reducer type. The gear changing device 2 comprises a casing 3. The gear changing device 2 comprises at least one pinion 41 mounted loose on the shaft 20. Each “loose” pinion 41 is arranged axially opposite one or more corresponding secondary radial conduits 23. Note that the shaft 20 passes through the casing 3 towards the outside of the gear changing device 2. The shaft is then driven in rotation, or drives in rotation, an element 4. For example, the element 4 is, or comprises, an electric machine. For example, the element 4 is an electric motor or an alternator. Element 4 is arranged outside of gear changing device 2. For example, arrangement 5 comprises element 4.

[0048] The shaft 20 comprises a first end 24. Preferably, the element 4 is arranged at the end of the shaft 20, on the side of the first end 24. For example, the axial hole 21 of the shaft 20 is formed from the first end 24 of the shaft 20, as illustrated in FIG. 6 in particular. The axial hole 21 is preferably plugged at the first end 24, for example by a plug 25. The plug 25 is for example a cylindrical metal pellet or capsule. The plug 25 is preferably force-mounted, fitted, for example shrunk, within a counterbore 26 formed at the end of the shaft 20.

[0049] Preferably, the arrangement 5 further comprises a pump 6 for discharging, supplying the oil to the conveying means 30. For example, the pump 6 is electric. Preferably, the pump 6 is arranged within the gear changing device 2, that is to say inside the device 2. The pump 6 is then connected directly, or indirectly, to the oil conveying means 30. By indirectly, it is meant for example that the oil discharged by the pump reaches the inlet 31 before reaching the conveying means 30. The pump is supplied by being immersed or by having an oil supply conduit immersed in an oil reserve also called a tank, for example at the bottom, at the bottom in the vertical direction, of the gear changing device.

[0050] For example, as illustrated in particular in Figures 3, 4 and 5, the bearing 10 is fixed to the casing 3. More precisely, the fixing of the casing 3 is ensured on, at the level of an inner face 7 of the casing 3. By “inner face” of the casing, we mean a face oriented towards the inside of the gear change device 2.

[0051] For example, fastening means 50, for example of the screw or bolt type, cooperate with holes 51 provided on the flange 18 and threads 53 or holes provided on the casing 3. Preferably, the flange 18 comprises radially extending lugs in which holes 51 are provided and the casing 3 comprises radially extending lugs in which threads 53 are provided. Preferably, the lugs, and consequently the corresponding holes and threads, are distributed at 120 degrees around the main axis AP. In this case, three screws 50 pass through the lugs of the flange 18 via the holes 51 and are screwed into the threads 53 of the casing 3 (see FIG. 3 in particular). Alternatively, fewer or more screws may be suitable. Alternatively, one or other fastening means may be suitable for fastening the bearing 10 to the casing 3.

[0052] Preferably, the inner face 7 of the casing 3 is a flat annular surface. Advantageously, a first seal 37 is provided to ensure sealing between a flat surface 19 of the bearing 10 and the inner face 7 of the casing 3. Preferably, the seal 37 is an O-ring. Alternatively, the seal is of square or rectangular section. Alternatively, the seal 37 is a flat seal extending over a substantial common area between the surface 19 of the bearing 10 and the inner face 7 of the casing 3 (case not illustrated).

[0053] The seal 37 is arranged in a circular groove formed in the surface 19 of the flange 18 of the bearing 10. Preferably the circular groove for receiving the seal 37 is centered on the main axis AP. For example, the section of the groove is square, rectangular or substantially forms a semicircle. Alternatively, or in addition, a circular groove is formed in the surface 7 of the casing 3. In this case, the seal can be arranged in the circular groove of the casing 3.

[0054] Advantageously, the casing 3 also comprises a centering bore 8 of suitable diameter, for example slightly greater than the diameter of the cylindrical external surface 13 of the cylindrical shoulder 12 of the bearing 10. Thus, the bearing 10 is centered relative to the casing 3 thanks to the shoulder 12 inserted, at least partially, within the centering bore 8 of the casing 3. Preferably, as illustrated in FIG. 5 in particular, the casing 3 also comprises a cavity 9, a hollow, a groove, opening into the centering bore 8. Advantageously, the cavity 9 extends over the entire depth of the bore 8 in the axial direction. In this case, preferably, the inlet 31 opens into the cavity 9, at least opposite the cavity 9, so as to supply the conveying means 30 with oil as illustrated in FIG. 4 by arrows corresponding to the oil flow F.As a reminder, the conveying means 30 comprises the circumferential external groove 14 formed on the external surface 13 of the shoulder 12. Advantageously, as illustrated in FIG. 4, the inlet 31 protrudes from the surface 19 towards the casing 3. More precisely, a tip or end 33 of the inlet 31 is found within the cavity 9 once the bearing is assembled on the casing 3. For this, preferably, a shoulder 34 is provided on the inlet 31 so as to facilitate the assembly of the inlet 31 on the bearing 10 and ensure an overhang of the end 33 less than the depth of the cavity 9 opposite this end 33. Thus, the cooperation of the end 33 of the inlet opening into the cavity 9 ensures an angular positioning of the bearing 10 relative to the casing 3 around the main axis AP.Thanks to this angular positioning, it is easy to provide at least one main radial hole 16 of the shoulder 12 opposite the cavity 9, which facilitates the passage of oil from the inlet 31 to the radial hole(s) opening into the cavity 9.

[0055] In summary, the inlet 31 communicates with the cavity 9. The cavity 9 communicates with the circumferential external groove 14 and, preferably, with at least one main radial hole 16. The circumferential external groove 14 communicates with the circumferential internal groove 15 via the main radial holes 16 in the shoulder 12. The circumferential internal groove 15 communicates with the main radial ducts 22 of the shaft 20. Thus, because the main radial ducts 22 open into the axial hole 21 of the shaft and the secondary radial ducts 23 also open into the axial hole 21, the oil is conveyed within the secondary radial ducts 23.Indeed, the conveying means 30 and the main radial conduit(s) 22 of the shaft 20 extend in the same plane, or substantially in the same plane A to facilitate, promote, maximize the passage of oil from the conveying means 30 to the axial hole 21 so as to supply the secondary radial conduit(s) 23 with oil.

[0056] Given the locations of the conduits 23 provided opposite the bearings of the “idle” pinions when the gear changing device 2 is assembled, the bearings of the “idle” pinions are lubricated by the oil coming from the intake 31. In order to guide the flow of oil and to avoid any oil leakage outside the gear changing device 2, a seal 42 is arranged in a bore provided in the casing 3, close to the element 4. The seal 42 comes into contact with the shaft 20, for example close to the shoulder 12. In order to guide the flow of oil, another seal 43 is arranged in a bore provided in the bearing 10. The bore for receiving the seal 43 has a diameter greater than the diameter of the second bore 17 and less than the diameter of the first bore 11 for receiving the rotational guide means 40. joint 43 is thus arranged, in the direction of the main axis AP, between the two bores 11, 17.Preferably, the seals 42, 43 are lip seals and / or sealing ring type seals.

[0057] In summary, thanks to the pump arranged in the gear change device, the entire oil circuit for lubricating the "idle" mounted pinion(s) remains internal to the gear change device. This internal layout facilitates the management of the sealing to be ensured with respect to this oil circuit. In the event of a possible leak in this circuit, it has no consequences since the leak is located within the gear change device which is able to collect oil, for example by being able to convey the oil from this leak to the tank.

[0058] Thus, the solution avoids arranging lubrication oil supply conduits and / or pipes outside the gear change device. As a result, any oil leakage external to the gear change device 2 linked to the lubricant supply to the idler gear bearings is avoided.

[0059] As seen previously, the solution allows an oil supply within the axial hole 21 of the shaft 20 compatible with the presence of the element 4 driven by the shaft 20, or driving the shaft 20, at the end 24 of the shaft 20. In addition, the solution allows the shaft 20 to be held by the bearing 10, in particular thanks to the first bore 11 for receiving the rotational guide means 40 of the shaft 20. Preferably, the supply of lubricating oil or tapping 31 can be arranged above the main axis AP of the bearing, or below this axis, or at another level.

[0060] As mentioned previously, the end 33 of the tapping 31 provides angular indexing of the bearing 10 during assembly by taking up position in the groove 9 of the casing 3.

[0061] As a reminder, the sealing of the lubrication circuit is ensured by the seals 42, 43 arranged on either side in the axial direction of the main radial holes 16 and the main radial conduits 22 once the casing 3, the shaft 20 and the bearing 10 are assembled with respect to each other. This sealing is completed by the seal 37 between the surfaces 7 and 19, respectively of the casing and the bearing. Thus, the seal 37 “isolates” the lubrication circuit from the rest of the gear change device 2, while the lip seals 42, 43 ensure the sealing between the rotating shaft 20 and the fixed bearing 10. Advantageously, as seen previously, the rotation guide means 40, preferably of the rolling bearing type, is fixed to the bearing 10. Furthermore, the plug 25 prevents any oil leakage from the axial hole 21 at the first end 24 of the shaft 20.As a reminder, the axial opening at the end 24 is provided with a view to producing, preferably machining, the axial hole 21.

[0062] During operation of the pump 6, the lubricant is conveyed via the tapping 31 to the chamber or cavity 9. Preferably, the flow rate of the pump allows the continuous filling of the cavity 9 by creating pressure within the circuit. In other words, forced lubrication is provided, i.e. coming from a closed circuit supplied by the pump, and not gravity lubrication by lubricant trickling. The circuit includes in particular the inlet 31, the cavity 9, the external and internal grooves 14, 15, the main radial holes 16, the main radial conduits 22, the axial hole 21 and the secondary radial conduit(s) 23 for ensuring the lubrication of the idler gear(s) 41. It should be noted that the pressure within the oil circuit is sufficient to counteract, oppose, the centrifugal force generated by the rotation of the shaft 20 which tends to expel the oil radially through its orifices or radial conduits 22, 23.In other words, the pressure in the lubricant circuit creates a centripetal force within the main radial holes 16 and the main radial conduits 22. The oil supply in the secondary radial conduits 23 is on the one hand pushed by the pressure provided by the pump, while being helped, facilitated by the centrifugal force resulting from the rotation of the shaft 20 to reach the level of the bearings of the idler gears 41.

[0063] As seen previously, the solution is particularly suitable for the presence of an element 4 at the end of the shaft 20, for example an electric machine. Indeed, the presence of such a machine at the end of the shaft has no effect on the lubrication circuit of the idler gears. The solution can be adapted to any architecture comprising an internal shaft opening outside the gearbox-type device in particular, in particular a shaft linked in rotation to an external element.

[0064] In addition, the solution offers a particularly short oil circuit. This short routing length offers a gain in terms of pressure drop. Since the circuit is internal, it is not necessary to protect certain circuit components against the risk of leaks.

[0065] Although the embodiment has a bearing fixed to a housing, the bearing and housing assembly may optionally constitute a single part, i.e. be in one piece. In this case, the sealing is ensured differently. Alternatively, the lubrication circuit is not arranged near a bearing, the support for the rotational guidance of the shaft then being arranged at a distance from the circuit. In this case, for example, the circuit, in particular the radial holes in the shoulder, the grooves and the ducts in the shaft, are arranged more cantilevered relative to the rotational guidance of the shaft.

[0066] In addition, the solution allows for a simple architecture at the level of a gear change device bearing, which facilitates possible internal maintenance of such a device.

[0067] As a remark, the solution therefore achieves the desired objective of allowing the optimal lubrication of an idler gear at the level of its contact zone with the shaft on which the idler gear rotates or translates and this despite the presence of at least one element arranged outside the gearbox at the end of the shaft supporting the idler gear, while being simple, reliable and economical and has the advantage of being able to be used on gearboxes of other types of motorized vehicles, namely trucks, buses, utility vehicles or even two-wheelers.

Claims

CLAIMS 1. Bearing (10) comprising: - a first bore (11) intended to receive a rotational guide means (40) for a shaft (20), - a second bore (17) intended to be traversed by such a shaft (20), the first and second bores (11, 17) being coaxial or substantially coaxial with a main axis (AP) of the bearing (10), the bearing (10) comprising a shoulder (12) extending radially from or substantially from the second bore (17), in particular coaxial with the main axis (AP), the shoulder (12) comprising an external surface (13), characterized in that the shoulder (12) comprises a conveying means (30) for pressurized lubricating oil from the external surface (13) to the second bore (17).

2. Bearing (10) according to the preceding claim, characterized in that the oil conveying means (30) comprises: - an external circumferential groove (14) formed in the external surface (13) of the shoulder (12), the external circumferential groove (14) extending in a plane (A) perpendicular to the main axis (AP) of the bearing (10), - an internal circumferential groove (15) formed in the second bore (17), the internal circumferential groove (15) extending in the plane (A), - at least one main radial hole (16) extending between the outer circumferential groove (14) and the inner circumferential groove (15).

3. Bearing (10) according to one of the preceding claims, characterized in that the bearing (10) comprises a flange (18), in particular extending radially from the shoulder (12), and in that an oil inlet (31), in particular of the conduit type, for supplying the conveying means (30) with oil passes through the flange (18).

4. Arrangement (5) comprising: - a shaft (20) extending coaxially or substantially coaxially with the main axis (AP) of a bearing (10), the shaft (20) comprising an axial hole (21), at least one main radial duct (22), and at least one secondary radial duct (23), the radial ducts (22, 23) opening into the axial hole (21), - a bearing (10) according to one of the preceding claims, the second bore (17) of the bearing (10) being crossed by the shaft (20).

5. Arrangement (5) according to the preceding claim further comprising: - a gear changing device (2) comprising a casing (3) and comprising at least one pinion (41) mounted loosely on the shaft (20) opposite the at least one secondary radial conduit (23), in particular a gear changing device (2) of the gearbox or reducer type, the shaft (20) passing through the casing (3) towards the outside of the gear changing device (2) so as to be driven in rotation or to drive in rotation an element (4), in particular an electric machine, arranged outside the gear changing device (2).

6. Arrangement (5) according to the preceding claim, characterized in that the arrangement (5) comprises a pump (6) for delivering oil under pressure, in particular an electric pump, arranged within the gear change device (2), the pump (6) being connected directly or indirectly to the oil conveying means (30).

7. Arrangement (5) according to claim 5 or 6, characterized in that the bearing (10) is fixed to the casing (3) at an inner face (7) of the casing (3).

8. Arrangement (5) according to one of claims 5 to 7, characterized in that the casing (3) comprises a centering bore (8) and in that the shoulder (12) of the bearing (10) is centered within this centering bore (8).

9. Arrangement (5) according to the preceding claim in combination with claim 3, characterized in that the casing (3) comprises a cavity (9) opening into the centering bore (8) and in that the inlet (31) opens into the cavity (9) so as to supply the conveying means (30) with oil.

10. Arrangement (5) according to one of claims 4 to 9, characterized in that the conveying means (30) and the at least one main radial duct (22) of the shaft (20) extend in the same plane or substantially in the same plane (A) perpendicular to the main axis (AP) of the bearing (10) to facilitate the passage of oil from the conveying means (30) towards the axial hole (21) so as to supply oil to the at least one secondary radial duct (23).

11. Arrangement (5) according to one of claims 4 to 10, characterized in that the axial hole (21) of the shaft (20) is formed from a first end (24) of the shaft (20), the axial hole (21) being closed at the first end (24), in particular by a plug (25).

12. Vehicle, in particular motor vehicle (1), characterized in that it comprises an arrangement (5) according to one of claims 4 to 11 or a bearing (10) according to one of claims 1 to 3.

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