FR2565645A1 - TORQUE TRANSMISSION DEVICE - Google Patents

Abstract

TORQUE TRANSMISSION DEVICE WITH AN ARRANGEMENT FOR ABSORBING OR COMPENSATION OF JUST USING AT LEAST TWO WHEELS MOUNTED COAXALLY THROUGH A BEARING, CAPABLE OF PRESENT A LIMITED ANGULAR TRAVEL AGAINST THE ACTION EXERCISED BY A SHOCK ABSORBER DEVICE INCLUDING A FRICTION SURFACE INTERACTING WITH A CLUTCH DISC. PROVISION 24 IS PROVIDED BETWEEN FRICTION SURFACE 4A AND BEARING 15 TO REDUCE THERMAL FLOW AT LEAST. THE INVENTION INCREASES THE LIFE OF THE BEARING AND THUS IMPROVES THE OPERATION OF THE TORQUE TRANSMISSION DEVICE.

Description

The present invention relates to a device for transmitting the

  couple with a provision for the absorption or compensation of

  strokes, and in particular of fluctuations in the torque of an internal combustion engine, with at least two flywheels coaxially mounted by means of a bearing, which may have limited angular deflection against the action exerted by a damping device , one of which can be connected to the internal combustion engine and the other of which can be connected by a friction clutch to the input part of a gearbox and has a friction surface interacting

with a clutch disc.

  It has already been proposed to provide in such torque transmission devices the bearing directly between the two wheels,

  so that when a bearing is used, a ring is

  rotate a steering wheel and the second ring of the second steering wheel.

  Although such torque transmission devices provide a very good damping vibrations appearing between

  the internal combustion engine and the. kinematic chain of a vehicle

  However, they have not been able to prevail until now in the construction

  because the life of the bearing is too short

  arranged between the wheels. This level constitutes one of the critical points

  such a device because the unfavorable conditions of service

  cause it to fail after a short period of service.

  The present invention relates to a torque transmission device having a better operation and a longer life than the aforementioned devices, and further allowing a

  particularly simple and economical production.

  According to an essential characteristic of the invention, a provision

  sition is provided, which reduces at least the heat flux between the friction surface and the bearing, whose thermal load is thus reduced. In-depth studies have shown that energy

  thermal release during the operation of the friction clutch pro-

  it causes a thermal stress on the bearing which is inadmissible in the long run. In case of use of low play bearings in particular, the differences in expansion and contraction of the various parts,

  resulting from very rapid heating and cooling,

  causing seizing phenomena of the bearing because the

  differences in temperature between the various parts of the bearing compensate for the play of the latter. An arrangement according to the invention allows a heating of the lubricant, such as oil, grease or other, always ensuring perfect lubrication of the bearing and by

  also a longer service life of the bearing.

  According to another particularly advantageous feature of the invention, the provision prohibiting an inadmissible heating of the bearing is an insulation between the friction surface and the

bearing.

  According to another particularly advantageous characteristic of the invention, the insulation is disposed between the bearing zone of the second flywheel, that is to say between the zone through which the second flywheel bears on the first through the bearing , and

  the bearing. Such an arrangement of insulation is particularly

  advantageous in the case of devices whose bearing comprises a bearing, because the insulation can then be provided between the or

  bearing rings carrying the second steering wheel, and secured in rotation

  the latter, and the bearing area of the steering wheel constituting a

  seat for bearing housing.

  Various materials make it possible to provide insulation that prevents overheating of the bearing. It is particularly advantageous to make such insulations in a reinforced plastics material

  where appropriate, or in a ceramic material. Thermo-materials

  curable materials, and in particular phenoplasts such as baking paper

  or thermoplastic materials, such as polytetrafluoro

  Ethylene, polyimide or polyamidimide are advantageously usable for carrying out isolations. The insulation can also be realized

in a reinforced polycarbonate.

  In particular in a torque transmission device whose steering wheel has an axial projection which penetrates axially into a central housing of the second wheel, the bearing being disposed between the projection and the housing, it is suitable for many applications

  to arrange the insulation between the central housing and the bearing.

  In other applications, for which a steering wheel has a

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  central trunnion which penetrates axially into a central housing of the second flywheel, the bearing being disposed between the trunnion and the housing, it is necessary to arrange the insulation between the trunnion and

the bearing.

  According to another particularly advantageous characteristic of the invention, the second wheel, which can be connected to the input part of a gearbox, has the central housing and the insulation is provided between said housing and a bearing ring. integral in rotation of said flywheel. According to another characteristic of the invention, the inner ring of the bearing is placed on the projection and the outer ring is mounted in the central housing.

  and carries the second steering wheel through the insulation.

  Various methods of fixing the insulation on the roller bushing

  The bearing may be advantageous depending on the material chosen.

  For example, insulation can be applied to

  let or sintered on the bearing or the bearing ring correspon-

  dante or, when it comes to insulating joints with an area

  sleeve shape, fitted on the bearing. According to another possibility

  advantageous advantage of achieving an insulation between the bearing and the corresponding flywheel, the bearing is pre-mounted on the corresponding flywheel, the outer ring being placed in a housing of diameter greater than the outer diameter of said ring, and the free space between the housing and the ring is filled by a plastic material

cast or sprayed.

  According to another particularly advantageous characteristic of

  the invention, the insulation is used simultaneously as a gasket

  sluggishness of the bearing. A seal of the bearing can be formed on the insulation. According to another advantageous characteristic of the invention, such an insulation with a seal consists of at least one L-section gasket, one of whose branches axially covers and surrounds a ring of the bearing, and whose other arm is extends radially towards the second ring of the bearing. according to

  another feature of the invention, the radial branch of the iso-

  L-section extends radially on at least a portion of the bearing ring which is not axially covered by the insulation and

  bears axially on said ring.

  It is suitable for many applications that the insulation consists of a single L-shaped joint, whose axial branch extends

  at least approximately the entire width of the roll ring

  is lying; it is nevertheless particularly advantageous for other applications that the insulation consists of two section joints

  in L, each placed on one side of one of the bearing rings.

  Especially in torque transmission devices

  a bearing is mounted in a central housing of the steering wheel pre-

  sensing the friction surface, and according to another characteristic of the invention, the L-section insulating joints have a branch directed - in the sectional view - radially inwards

  and are placed on the outer ring of the bearing.

  In order to ensure perfect sealing of the bearing, and according to another particularly advantageous feature of the invention,

  the radial branch of the insulating joints ensuring the tightness of the

  lement is axially loaded by a force accumulator to the bearing ring radially covered by said branch, which is thus applied to the front face of the bearing ring. Such a force accumulator can usefully be constituted by a Belleville spring. It may also be appropriate to make the L-shaped insulating joint so that, when it is mounted on the bearing, the radial branch is elastically strapped and thus bears elastically.

  on the bearing ring that it covers radially.

  If a Belleville spring is used to load the radial sealing branch of the insulation, and according to another characteristic of the invention, the Belleville spring is supported, by its outer radial end, on the second flywheel which can be connected to the input part of a gearbox, and charge

  axially, by its inner radial end, the end zones

  mite of the radial branch of the seal.

  According to another characteristic of the invention particularly advantageous for mounting, the insulation has a sleeve-shaped zone, which is fitted into the bearing housing in one of the flywheels. Depending on the application, first insert the insulation in the housing, then the bearing, or first mount the insulation on the bearing and then press it into the housing. According to another characteristic of the invention, the region of the sleeve-shaped insulation surrounding the bearing presents - view along the axis - zones of different thickness or diameter so that only the zones with larger diameter or thickness are

  secured in the bearing housing by interference fit.

  In the case of the use of bearings filled with lubricant, and according to another particularly advantageous characteristic, an additional seal is provided between the branch of the L-joint.

  covering axially and surrounding one of the rings of the bearing and la-

  said ring, and prohibits any possibility of escape of the lubricant between the insulation and the bearing ring, under the action of forces

  centrifugals for example. Such a seal may advantageously

  consist of an O-ring. The seal then bears on the inner envelope surface of the axial branch of the insulation and is housed in a recess, such as a chamfer or

  a groove in the outer ring of the bearing. According to another characteristic

  of the invention, the seal is clamped between the end face of the axial leg of the insulation and a shoulder of

the outer ring of the bearing.

  In order to ensure easier assembly and easier centering between the flywheels, taking into account the manufacturing tolerances, and according to another advantageous characteristic of the invention, an insulating seal of conical section is arranged between the bearing zone of the second

  steering wheel and the bearing or corresponding ring of the bearing. The rou-

  and / or the load-bearing zone have a different

  of the invention, a conical envelope surface adapted to the seal

  insulating. In order to ensure automatic compensation of possible wear

  and a perfect centering and holding of the bearing in its housing, and according to another characteristic of the invention, the conical section insulating seal is subjected to an axial pretension force directed towards the apex of the cone, so that it gets stuck between the housing and the corresponding ring of the bearing. To assure

  a perfect jamming of the insulating joint, and according to another characteristic

  of the invention, the insulating joint is split, that is to say

open on its periphery.

  An insulating seal of conical section may naturally also have a bearing seal and be loaded axially

  by a force accumulator to the front face of the wheel ring.

  on which the seal is supported.

  Other features and advantages of the invention will be

  better understood using the following detailed description of

  Embodiments and accompanying drawings in which: Figure 1 is a section of a torque transmission device according to the invention; and

  Figures 2 and 3 show other arrangements according to the invention.

  to reduce the heat flux between the friction surface and

  the bearing of a torque transmission device.

  As shown in Figure 1, the device 1 for compensation of torque surges includes a flywheel 2, which is divided into two flywheels 3 and 4. The steering wheel 3 is fixed by screws 6 on the crankshaft of an engine internal combustion not shown. A friction clutch 7 is fixed by a means not shown on the flywheel 4. A clutch disk 9, mounted on the primary shaft 10 of a gearbox, not shown, is provided between the pressure plate 8 of the friction clutch 7 and the flywheel 4. A Belleville spring 12, pivotally mounted on the cover 11 of the clutch, charges the

  pressure plate 8 of the friction clutch 7 towards the steering wheel 4.

  The operation of the friction clutch 7 makes it possible to secure and disengage the flywheel 4 and consequently also the flywheel 2 of the primary shaft 10 of the gearbox. Damping means are provided between the flywheel 3 and the flywheel 4, in the form of a damping device 13 in series with a torque limiter coupling 14, which allow limited angular travel of the two flywheels 3 and 4. Both flywheels 3 and 4 are mounted on a bearing 15 allowing

  a relative rotation. The bearing 15 comprises a rolling bearing

  16. The outer ring 17 of the bearing 16 is mounted in a bore 18 of the flywheel 4 and the inner ring 10 on a central cylindrical pin 20 of the flywheel 3, moving axially away.

  of the crankshaft 5 and penetrating into the bore 18.

  The inner ring 19 of the bearing is mounted on the journal 20 by a fit with interference and clamped axially between a shoulder 21 of the journal 20 or the flywheel 30 and a lock washer.

  22, which is fixed by screws 23 on the front face 20a of the door.

rillon 20.

  Thermal insulation 24 is provided between the outer ring 17 of the bearing and the flywheel 4 to interrupt or at least reduce the heat flow between the friction surface 4a of the steering wheel.

  4, interacting with the clutch disc 9, and the bearing 16.

  This prevents excessive thermal loading of the grease filling the bearing and thermal deformation too

  large or inadmissible dilatation of the bearing, which risks

  drag a jamming of the balls 16a between the rings 17 and 19 of the bearing. To receive the insulation 24, the bore 18 of the flywheel 4 has a larger diameter than the outer diameter of the outer ring 17 of the bearing, so that a radial gap is

form.

  The insulation 24 is constituted by two seals 25,26 with section

  in L, each mounted on one side on the outer ring 17 of the bearing.

  The branches 25a, 26a axially facing the insulating joints 25, 26

  L-section cover or surround the outer ring 17 of the wheel

  LEMENT. The branches 25b, 26b directed radially inwards

  extend in part radially on the inner ring 19 of the wheel.

  and to bear axially on the latter, so that they serve simultaneously to seal the bearing 16. In order to ensure perfect sealing of the bearing 16, the radial branches 25b, 26b are each loaded axially towards the end faces of the inner ring 19 of the bearing by an accumulator

  of force constituted by a spring Belleville 27, 28. The spring Bel-

  Leville 27 bears radially on the outside on a shoulder of a disk 30, secured to the second wheel 4 by columns 29, and radially inwardly loads the end regions of the radial branch 25b of the gasket. Similarly, the Belleville spring 28 bears radially on the outside on a shoulder of the flywheel 4 and radially inwards the end zones of the radial branch 26b of the insulating gasket 26. the embodiment according to Figure 1, it is advantageous for the assembly of the seals 25, 26 and the bearing 16, first to press the area of the bush-shaped seals on the outer ring 17 of the bearing, and then to press the bearing 16 carrying the seals 25, 26 fitted into the bore or the housing 18 of the flywheel 4. The axial locking of the bearing 16 relative to the flywheel 4 is effected by axial clamping between a shoulder 31 of the flywheel 4 and the disc 30 ,

  with interposition of the seals 25, 26.

  The damping device 13 comprises two disks 30, 33 dis

  placed on either side of the flange 32 and secured in rotation with axial separation by the balancers 29. These serve

  in addition for fixing the two discs 30, 33 on the steering wheel 4.

  The disks 30, 33 and the flange 32 have notches in which are stored force accumulators constituted by coil springs 34. These force accumulators 34 are opposed to

  relative rotation of the flange 32 and the two disks 30, 33.

  The damping device 13 further comprises a friction 13a through which acts the possible angular displacement of the two flywheels 3 and 4. The friction 13a is disposed axially between the disc 30 and the flywheel 3, and comprises a force accumulator 35, constituted by a Belleville spring maintained with a tire between the disc 30 and a pressure ring 36, so that the friction ring 37 disposed between the pressure ring 36 and the wheel 3 is tightened. The bearing 16 absorbs the force exerted by the spring

Belleville on the record 30.

  The flange 32 constitutes, on the one hand, the input part of the damping device 13 and, on the other hand, the output part of the torque limiting coupling 14. The input part of this torque limiting coupling 14 is constituted by two disks 38, 39 presenting a

  axial and integral spacing in rotation of the steering wheel 3. The annular disc

  39 is fixed by rivets 40 on the steering wheel 3. The disc 38 pre-

  on its periphery are axial lugs 38a which engage in notches 41 of the disk 39 for the rotational locking of the disk 38 with respect to the disk 39. Radial arms 42 of the flange 32 are clamped axially between the disks 38, 39 To do this, a Belleville spring 43 clamps the two discs 38, 39 towards each other. The Belleville spring 43 engages one hand on the flywheel 3 and on the other hand the disk 38 to the disk 39. In the area between the arms 42 of the flange 32, the disks 38, 39 have aligned notches axially and containing force accumulators 44, which constitute end stops for the arms

  of the flange 32 and thus limit the angular clearance of the accou-

torque limiter 14.

  In the alternative embodiment shown in FIG. 2, a ball bearing 116, arranged in the same way as the ball bearing 16 according to FIG. 1, is again used for mounting the steering wheel 4 with respect to the steering wheel 3. The bushing 117 of the ball bearing 116 has chamfers 117a, 117b, so that

  free spaces are formed between said ring 117 and the insulated joints

  lants 125, 126 which cover axially. Seals formed by O-rings 145, 146 are provided in these free spaces. These O-rings 145, 146 prevent backflow or leakage of the bearing grease between the L-joints 125, 126 and the bearing ring 117. The chamfers 117a, 117b and the O-rings 145, 146 are mutually adapted so that the O-rings are elastically deformed between the seals 125, 126 to

  section L and the chamfers 117a, 117b of the bearing 116.

  As further shown in Figure 2, the radial branches b, 126b L-section insulating and sealing joints 125, 126 have a reduced thickness compared to that of the axial branches 125a, 126a. A sealing heel 125c, 126c is formed on

  the inner radial end of the branches 125b, 126b.

  In the embodiment shown in FIG. 3, an insulating joint 225 of conical section is disposed between the housing 218 of the flywheel 4, which receives the bearing 216, and the outer ring

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  217 of this bearing. In this embodiment, the surfaces

  outer and inner shells of the insulating joint 225 are coni

  following the axial direction. However, it would be possible without difficulty to make this joint with a single conical envelope surface. The housing 218 is adapted to the conical outer envelope surface and the outer envelope surface of the bearing ring 217 is adapted to the conical inner envelope surface of the insulating joint 225. The latter is axially loaded, towards the top of its cne, by a Belleville spring 227 which bears on the disc 230, fixed axially with respect to the flywheel 4. The insulating joint 225 has a zone 225b directed radially inwards and sealing the bearing by bearing axially on the inner ring 219 of this last. The seal on the other side of the bearing is provided by a seal 226 made of insulating material, which the Belleville spring 227 closes axially between the outer race 217 of the bearing and a shoulder 231 of the flywheel 4. The seal 226 comprises a

  heel 226b which bears axially on the inner ring 219.

  The exemplary embodiments according to FIGS. 1 and 2 comprise Belleville springs 27, 28 which axially load, towards the ring 19 or 119 of the bearing, the radial sealing zones 25b, 26b or b, 126b. However, a suitable selection of the material would also make it possible to make the joints 25, 26 and 125, 126 so that their

  radial branches 25b, 26b or 125b, 126b are deformed elastically

  after installation and thus apply axially with pretension on the ring 19 or 119 of the bearing. This provision would

  to remove Belleville springs 27, 28.

  In the embodiments described above, the insulation consists of seals arranged between the second wheel 4 and the bearing 16, 116 or 216. According to other forms not shown in FIG.

  embodiment of the invention, the insulation may, however, be spraying

  Sealed or sintered on the bearing 16, 116, 216 or its ring 17, 117, 217, so that the insulation forms substantially one piece with the bearing. The insulation could likewise be deposited on the surface

housing envelope 18, 118, 218.

  il, 2565645 When using bearings with seals, for example, as proposed by the bearing manufacturers, it is also possible to pre-assemble the bearing 16 on the flywheel 4 as follows: The ring 17 is centered and maintained in the housing 18, greater in diameter than the outer diameter of said ring 17, and the free space between the housing 18 and the

  ring 17 is filled with a plastic material or a synthetic resin

that poured or sprayed.

  Of course, various modifications may be made by those skilled in the art to the principle and to the devices which have just been described solely by way of nonlimiting examples, without

depart from the scope of the invention.

Claims (38)

claims   1. Torque transmission device with a provision for absorbing or compensating for jolts, and in particular for fluctuations in the torque of an internal combustion engine, with at least two flywheels coaxially mounted via a bearing, which may have a limited angular travel against the action exerted by a damping device, one of which can be connected to the internal combustion engine and the other can be connected by a friction clutch to the input part of a gearbox and has a friction surface interacting with a   clutch disk, said device being characterized by a   position (24; 125,126; 225,226) reducing at least heat flux   between the friction surface (4a) and the bearing (15).   Torque transmission device according to claim 1, characterized in that the arrangement consists of an insulation between   the friction surface (4a) and the bearing (15).   Transmission device, torque according to one of the claims   i or 2, characterized in that the insulation is disposed between the bearing zone (18, 118, 228) of the second flywheel (4) and the bearing (16, 116, 216).   4. Torque transmission device according to any one of   Claims 1 to 3, the bearing of which consists of a bearing   (16, 116, 216) and characterized in that the insulation (24; 125, 126; 225, 226) is disposed between the one or more rings (17, 117, 217) carrying the second flywheel (4) -and solidarity with the latter, and housing   (18, 118, 218) of the bearing in said flywheel (4).   5. Torque transmission device according to any one of   Claims 1 to 4, characterized in that the insulation (24; 125, 126;   225, 226) is made of plastic.   6. Torque transmission device according to any one of   Claims 1 to 4, characterized in that the insulation (24, 125,   126; 225, 226) is made of a ceramic material.   7. Torque transmission device according to any one of   Claims 1 to 5, characterized in that the insulation (24;   126; 225, 226) is made of a thermosetting material such as   than a phenoplast, paper bakélisé for example.   8. Torque transmission device according to any one of   Claims 1 to 5, characterized in that the insulation (24;   126; 225, 226) is made of a thermoplastic material, such as polytetrafluoroethylene, polyimide or polyamidimide. 9. Torque transmission device according to any one of   Claims 1 to 5, characterized in that the insulation (24;   126; 225, 226) is made of reinforced polycarbonate.   10. Torque transmission device according to any one of   1 to 9, one of the rims has a protrusion   axis that enters a central housing of the second wheel and whose   the bearing is disposed between the projection and the housing, said arrangement   characterized in that the insulation (24; 125, 126, 225, 226) is disposed between the central housing (18, 118, 218) and the bearing (16, 116, 216).   11. Torque transmission device according to any one of   Claims 1 to 9, a flywheel having a central projection   of the trunnion type that enters a central housing of the second   steering wheel and whose bearing is arranged between the trunnion and the housing   said device being characterized in that the insulation is   disposed between the trunnion and the bearing.   12. Torque transmission device according to any one of   Claims 1 to 11, characterized in that the second wheel (4),   which can be connected to the input part (10) of a gearbox, has the central housing (18, 118, 218) and the insulation (24; 125, 126; 225, 226) is disposed between said housing and a ring (17;   117, 217) of rotationally integral bearing said flywheel.   13. Torque transmission device according to any one of   Claims 1 to 12, characterized in that the inner ring   (19, 119, 229) of the bearing (16, 116, 216) is placed on the projection   (20) and the outer ring (17, 117, 217) is mounted in the box.   center (18, 118, 218) and carries the second steering wheel (4) by   intermediate of the insulation (24; 125, 126; 225, 226).   14. Torque transmission device according to any one of   Claims 1 to 13, characterized in that the insulation is applied spray on the bearing.   15. Torque transmission device according to any one of   Claims 1 to 13, characterized in that the insulation is sintered on the bearing.   16. Torque transmission device according to any one of   Claims 1 to 13, characterized in that the insulation (24;   126) is fitted on the bearing (16, 116).   17. Torque transmission device according to any one of   Claims 1 to 16, characterized in that the bearing (16) is   preassembled on one of the wheels (4), the outer ring (17) being   placed in a housing (18) of greater diameter than the outer diameter   of said ring (17), then the free space between the housing (18) and the ring (17) is filled by a plastic casting material or sprayed.   18. Torque transmission device according to any one of   Claims 1 to 17, characterized in that the insulation (24;   126; 225, 226) serves simultaneously as a seal of the bearing (16, 116, 216).   19. Torque transmission device according to any one of   Claims 1 to 18, characterized in that a seal   (25b, 26b, 125b, 126b, 225b, 226b) of the bearing (16, 116, 216) is   formed on the insulation (24; 125, 126; 225, 226).   20. Torque transmission device according to any one of   Claims 1 to 19, characterized in that the insulation (24;   126; 225, 226) is constituted by at least one L-section gasket (25, 26), one leg (25a, 26a; 125a, 126a; 225a) axially covering and surrounding a bearing ring (17, 117, 217). , and whose other branch (25b, 26b, 125b, 126b, 225b) extends radially towards   the second ring (19; 119, 219) of the bearing.   Torque transmission device according to claim 20, characterized in that the radial branch (25b, 26b, 125b, 126b, 225b) of the L-shaped insulation (24; 125, 126; 225) extends radially on a longitudinal axis. at least part of the ring (19, 119, 219) of the bearing, which is not covered axially by the insulation, and bears axially on said ring (19, 119, 219).   22. Torque transmission device according to any one of   Claims 1 to 21, characterized in that the insulation is con-   formed by two L-section seals (25, 26; 125, 126) placed   each on one side on one of the rings (17; 117) of the bearing.   23. Torque transmission device according to any one of   claims I to 22, characterized in that the insulating   L-section (25,26; 125,126; 225) have a branch (25b, 26b, 125b, 126b, 225b) directed to the cross-sectional view radially inward and are placed on the outer ring (17). , 117 217) of the bearing.   24. Torque transmission device according to any one of   Claims 1 to 23, characterized in that the radial branch (25b,   26b, 125b, 126b, 225b) insulating joints (25, 26; 125, 126; 225) are loaded axially by a force accumulator (27, 28, 227) towards the ring (19, 119, 219) of the bearing covered radially by said branch.   Torque transmission device according to claim 24, characterized in that the force accumulator is constituted by a Belleville spring (27, 28, 227).   26. Torque transmission device according to one of the claims   24 or 25, characterized in that the Belleville spring (27, 28) is supported, by its outer radial end, on the second wheel (4), which can be connected to the input part (10) of a box of speeds, and axially load, by its inner radial end, the end zones of the radial branch (25b, 26b) of a joint sealing (25, 26).   27. Torque transmission device according to any one of   Claims 1 to 26, characterized in that the insulation (25, 26;   126) has a bush-shaped zone (25a, 26a, 125a, 126a) which is fitted into the bearing housing (18, 118) (16, 116) in one of the ruffles (4).   28. Torque transmission device according to claim 27, characterized in that the insulation (24) is first made on the bearing (16, 116) and then fitted with the latter in the housing. (18, 118) of one of the wheels (4).   29. Torque transmission device according to any one of   Claims 1 to 28, characterized in that the zone of the insulation   in the form of a sleeve surrounding the rolling bearing present - view along the axis of the zones of different thickness or diameter, so that only the zones with larger diameter or thickness are fixed   in the bearing housing by a tightening fit.   30. Torque transmission device according to any one of   Claims 1 to 29, characterized by a seal (145,   146) provided between the leg (125a, 126a) of the L-shaped gasket (125, 126) axially covering and surrounding one (117) of the bearing rings and said ring (117).   Torque transmission device according to claim 30, characterized in that the seal is constituted by a O-ring (145, 146).   Torque transmission device according to one of the claims   29 or 30, characterized in that the seal (145, 146) bears on the inner envelope surface of the axial leg (125a, 126a) of the insulation (125, 126) and is housed in a recess, such   a chamfer or groove in the outer ring (117) of the wheel is lying.   33. Torque transmission device according to one of the claims   or 31, characterized in that the seal is clamped between the end face of the axial leg of the insulation and a shoulder   the outer ring of the bearing.   34. Torque transmission device according to any one of   Claims 1 to 33, characterized by an insulating seal (225) of   conical section disposed between the bearing area (218) of the second steering wheel (4) and the bearing (216).   Torque transmission device according to claim 33, characterized in that the bearing (216) and / or the bearing zone   (218) have a conical envelope surface adapted to the lant (225).   36. Torque transmission device according to one of the claims   33 or 34, characterized in that the insulating joint (225) of conical section is subjected to an axial pretensioning force, directed towards the summit of the c3ne.   37. Torque transmission device according to any one of   Claims 33 to 35, characterized in that the insulating joint is   split, that is to say open on its periphery.   38. Torque transmission device according to any one of   Claims 33 to 36, characterized in that the insulation (225)   carries a sealing joint (225b) of the bearing (216) and is made   or disposed according to any one of claims 20 to 26.