FR2626636A1 - TORQUE TRANSMISSION DEVICE - Google Patents

Abstract

Torque transmission device for an internal combustion engine, comprising a flywheel subdivided into two inertia masses which can rotate, by means of a rolling bearing, against the action of a damping device. According to the invention, there is provided an arrangement 24 reducing at least the heat flow between the friction surface 4a and the bearing 15: this arrangement is made in the form of at least one ring 25, 26 with an L-shaped section, of which one branch axially covers at least part of one 17 of the rings of the bearing, while the other branch, which extends radially, bears axially on the other ring 19 of the bearing and is charged by a force accumulator 27 towards said other ring 19 of the bearing. 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 absorption.a, the compensation of

  strokes, and in particular fluctuations in the torque of a teacher to

  internal combustion, with at least two flywheels mounted happily -

  by means of a bearing, which can exhibit a 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 a input part of a gearbox and presents a mne interacting friction surface

with a clutch disc, -

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

  so that when using a bearing, a ring is

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

  Although such torque transmission devices allow to obtain a very good damping of vibrations appearing entered

  the internal combustion engine and kinematic chat of a vehicle

  However, they have not been able to impose themselves so far in the

  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

  lead to its failure after a short period of service.

  The present invention has as its object a torque transmission device exhibiting better operation and longer life than the aforementioned devices, and furthermore allowing a

  particularly simple and economical production.

  According to an essential characteristic of the inventions, 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

  heat released during the operation of the friction clutch pro-

  a thermal stress of the inadmissible ruler.

  long. In case of use of low clearance bearings in particular,

  the differences in expansion and contraction of the various parts, -

  resulting from very rapid heating and cooling, -

2 6 2636 6 -

  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 characteristic of

  the invention, the provision prohibiting 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

  lise, or thermoplastic materials, such as polytetrafluoro

  Ethylene, polyimide or polyamidimide are advantageously usable for the realization of 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 in 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 central yoke that penetrates axially into a central housing of the second wheel, the bearing being. has between the trunnion and. housing, the insulation between the trunnion and

the bearing.

  According to another particularly advantageous feature 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 bushing. solidarity bearing in rotation of said flywheel. According to another feature 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 to 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 'en

  sleeve shape, e-grip on the bearing. According to another possibility

  advantageous bilitâ to achieve 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 projected to the pistolest.

  According to another particularly advantageous characteristic of

  invention, isotation is used at the same time as a seal of

  sluggishness of the bearing. For this purpose, a seal of the bearing can be shaped on the insulation. According to another advantageous characteristic of the invention, such an insulation with a seal is provided by at least one L-section seal, one branch axially covering and surrounding a bearing ring, and the other branch and extends radially towards the second ring of the bearing. According to another feature of the invention, the radial branch of the L-shaped insulation extends radially on a portion of the bearing ring which is not axially covered by the insulation and

  bears axially on said ring.

  It is appropriate for many applications that the insulation is constituted by 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 on 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 may usefully be a Belleville spring. It may also be appropriate to make the insulating seal an L so that, when mounted on the bearing, the radial arm is elastically bandaged 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 load

  axially, by its inner radial end, the end zones

  mite of the radial branch of the seal.

  According to another characteristic of the invention which is particularly advantageous for mounting, the insulation has a sleeve-shaped zone, which is fitted into the bearing housing in one of the flywheels. According to the application, it is necessary first to insulate the insulation in. the housing, then the bearing, or first mount the insulation on the bearing and then insert it into the housing. According to another rare feature of the invention, the zoe of the sleeve-shaped insulation surrounding the bearing has a view along the axis of areas of varying thickness or diameter so that only areas of greater diameter or thickness are secured in the bearing housing by a tightening 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-shaped seal

  covering ax / alement and surrounding one of the rings-the bearing and the-

  said ring, and prohibits any possibillt of escape of the lubfactory if the insulation and the hague of the bearing, under the action of pranks

  centrifugals for example. Such seal seal can advantageously

  may be constituted by an O-ring. The sealing gasket then bears against the inner envelope surface of the axial branch of the insulation and is housed in a recess, such as a chanifreln or

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

  Inertia, the seal is tight between the front 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 entry between the flywheels, taking into account the manufacturing tolerances, and according to another advantageous characteristic of the invention, an insulating seal of tonic section is arranged between the zone carrying the second part and the second part.

  steering wheel and the corresponding bearing or bearing of the bearing.

  and / or the airfoil according to another tick characteristics of the invention, a conical envelope surface adapted to the seal

  insulating. In order to ensure automatic compensation of possible wear

  As well as perfect centering and holding of the bearing in its housing, and according to another feature of the invention, the insulating ring section seal is subjected to an axial pretensioning force directed towards the top of the pipe, so that gets caught between the housing and the corresponding ring of the bearing. In order to ensure

262 & 636

  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 gasket 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 sectional view 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 FIG. 1, the torque compensation device 1 comprises a flywheel 2, which is divided into two flywheels 3 and 4. The flywheel 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 groove 18 of the volau 4 and the inner ring 10 on a cylindrical spigot 20.central -volant 3, away ax.alemet

  crankshaft 5 and penetrating the bore 18.

  The inner ring 19 of the roulemet is mounted on the trunnion 20 by a clamping fit and clamped axemént between a shoulder 21 of the t. urillon 20 or steering wheel 30 and a lock washer

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

rillon 20.

  A thermal insulation 24 is pre-curved between the outer ring

  17 of the bearing and the steering wheel 4 to interrupt -or anyway

  reduce the heat flux between the friction surface 4a; the flywheel 4, interacting with the clutch disc 9, and the bearing 16 ..: This prevents excessive thermal loading of the grease filling the bearing and a thermal deformation too

  large or inadmissible dilatation of the bearing, which risks

  drag a wedging of the balls 16a between your rings 17 and 19 of the

  aoulement. To receive the insulation 24, lange 18 of the steering wheel 4-

  has a diameter greater than the outside diameter of the outer ring 17 of the bearing, so that a radial interstice is

form.

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

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

  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 towards 1 interior

  extend partly radially on the inner ring 19 of the wheel

  and axially support the latter, that they simultaneously serve as seal-été-héité roaulement 16. In order to ensure perfect sealing of the bearing 16, the radial branches 25b, 26b are each loaded axially to the front faces of the inner ring 19. of the bearing by an accumulator

  Bellieville spring 27, 28. The spring Bel-

  Leville 27 bears radially on the outside on a shoulder of a disc 30, secured to the flywheel seoeand 4 by coloanettes 29, and radially inwardly loads the end zones of

2626636.

  the radial branch 25b of the insulating gasket 25. Likewise, the Belleville spring 28 bears radially on the outside on a shoulder of the flywheel 4 and radially loads inside the end zones of the radial branch 26b of the insulating gasket 26. In the embodiment according to Figure 1, it is advantageous for the mounting of the seals 25, 26 and the bearing 16 to first press the zone of the socket-shaped seals on the outer ring. 17 of the bearing, 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 steering wheel 4 and the disc 30,

  with interposition of seals Z5, 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

  Fig. 39 is shown by faders 40 on the fly 3. The disk 38 pre-

  on its lug around the axial lugs 38a which engage in latches 41 of the disk 39 for the rotational locking of the disk 38 relative 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 takes one hand on the steering wheel 3 and on the other hand the disk 38 to the. In the region between the arms 42 of the flange 32, the discs 38, 39 have axially aligned indentations and contain force accumulators 44, which constitute end stops for the arms.

  of the flange 32 and thus limit the angular deflection of the

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

  slow 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 toric seals 145, 146 are adapted so that the O-rings are resiliently deflected between the seals 125, 126 through.

  L-section and bevels 117a, 117b of the bearing It6.

  As further shown in FIG. 2, the radial branches b, 126b of the insulating and sealing joints 125, 126 have an L-shaped cross section which has a reduced thickness relative to that of the axial threads 125a, 126a. A sealing heel 125c, 126c is formed on

  The inner radial end of branches 25b 12, 6h.

  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

2, 26636.

  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 casing surface and the outer casing surface of the ring 217 of the bearing is adapted to the conical inner casing surface of the insulating joint 225. The latter is axially loaded, towards the apex of its cone, by a Belleville spring 227 which bears on the disc 230, fixed axially relative 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 226h 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

  16, 116 or 216. According to other unrepresented forms of

  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.

  In the case of the use of rolling bearings, for example, as proposed by the bearing manufacturers, it is also possible to pre-mount the bearing 16 on the flywheel 4 as follows: The outer ring 17 is and held in the housing 138, of diameter greater than the outer diameter of said ring 17, and the free space between the housing 18 and the

  ring 17 is filled with plastic material and synthetic risin

that poured or sprayed.

  Of course, various modifications can be brought by the art to the principle and the devices that have been described as non-limiting examples, without

depart from the scope of the invention.

Claims (19)

  1. Torque transmission device for an internal combustion engine, comprising a flywheel subdivided into two rotating masses of inertia, by means of a rolling bearing, against the action of a device damper, namely a first mass of inertia which can be rigidly connected to the driven shaft of the engine-internal combustion, and a second mass of inertia, which has a friction surface intended there to be applied against a disk of clutch and to which can also be attached a friction clutch coupling the second mass of inertia to a gearbox and uncoupling thereof, characterized in that there is provided a provision (24; 125, 126; 225 , 226) reducing at least the heat flux from the friction surface (4a) towards the bearing (15), and made under the fort of at least one ring (25, 26) with an L-section and a branch axially covers at least a part of a (17; 117; 217) bearing rings, while the other branch, which extends radially bears axially on the other ring (19; 119; 219) of the bearing and is loaded by a force accumulator (27, 28, 227) towards said other ring (19; 119; -219) of the bearing.   Torque transmission device according to Claim 1, characterized in that the accumulator of the invention is Belleville (27, 28 = 227).   3. Torque transmission device according to one of the   Claims I or 2, characterized in that the Belleville spring (27, 28)   radially outwardly supports, on the second mass of inertia (4) which can be connected to the input part (10) of a gearbox, and load axially, internally from the radial point of view, the   end regions of the radial branch (25b, 26b) of a sealing ring 30. Chéité (25, 26).   4. Torque transmission device according to any one   Claims 1 to 3, characterized in that the insulation (25, 26; 125, 126)   has a sleeve-like zone (25a, 26a; 125a, 126a) forcibly inserted into the housing (18; 118) which receives the bearing (16);   116), of one of the masses of inertia (4).   5. Torque transmission device according to any one   Claims 1 to 4, characterized in that the insulation (24) is   firstly fitted on the bearing (16; 116) and then force-fitted, together with the bearing, into the housing (18, 118) of one (4) of the masses of inertia. 6. Torque transmitting device according to any one of   claims I to 5, characterized in that a de-tightness joint (145,   146) is provided between the leg (125a, 126a) of the L-section ring (125, 126>, which axially covers and surrounds one (-17) of the bearing, and this ring (117).   Torque transmission device according to Claim 6, characterized in that the seal is formed by a ring O-ring (145, 146).   8. Torque transmission device according to claim 6 or 7, characterized in that the seal-seal (145, 146) is supported on the lower envelope surface of the axial branch (125a, 126a) of the insulation (125). , 126), and is housed in a recess, such as a chamfer or   a groove of the outer ring (I17) of the bearing.   9. Torque transmission device according to any one   Claims I to 8, characterized in that the insulation (24; 125, 126;   225, 226) serves simultaneously as a seal for the bearing (16 i 1 16; 216).   10. Torque transmission device according to any one   claims 1-. 9, characterized in that a seal (21,   26b; 125b, 126b; 225b, 226h) for the bearing (16 116; 216) is formed   on the insulation (24; 125, 126; 225, 226).   11. Transmission device of the couple-selion any one   claims I to 10, characterized in that the insulation is formed by   two L-section rings (25, 26; 125, 1261), which are each arranged   on one side of one of the rings (17; 117) of the bearing.   12. Torque transmission device according to any one of   claims I to 11, characterized in that the insulating rings to   cross-sectional section L (25, 26; 125, 126 225) have a branch (25b, 26b; 125b, 126b; 225b) directed towards the cross-section radially inwards, and are placed on the outer race (17; 117; 217) of the bearing 13. Torque transmission device according to any one of   Claims 1 to 12, characterized in that the insulation is arranged   between the bearing zone (18; 118; 218) of the second mass of inertia (4) and the bearing (16; 116; 216).   14. Torque transmission device according to any one   Claims 1 to 13, in which the bearing is constituted by a bearing   bearing (16; 116; 216), characterized in that the insulation (24; 125; 126 6; 225; 226) is provided between the bearing ring (17; 117; 217) carrying the second mass inertia (4) and are integral in rotation with this mass, and the housing (18; 118; 218) serving to receive the   rolling, of this mass of inertia.   15. Torque transmission device according to any one of   Claims I to 14, characterized in that the insulation (24; 125, 126   225, 226) is made of plastic.   16. Torque transmission device according to any one of   claims I to 15, wherein one of the masses of inertia has   an axial projection, which enters a central housing of the other mass of inertia, and the bearing is disposed between the projection and the housing, characterized in that the insulation (24; 125, 126; 225, 226) is arranged between the   central housing (18; 118; 218) and the bearing (16; 116; 216).   17. Torque transmission device according to any one   claims I to 16, wherein one of the masses of inertia has   a central projection of the trunnion type, which penetrates, in the axial direction, into a central recess of the other mass of inertia, and the bearing disposed between the trunnion and the housing, characterized in that the insulation is   disposed between the journal-like projection and the bearing.   18. Torque transmission device according to any one of   claims I to 17, characterized in that the second mass of inertia   (4), which can be connected to the input part (10) of a gearbox, : .-   has a central housing (1; 118; 218), and the insulation (24; 125s; 126; 225; 226) is provided between this housing (18,118,218) and a bushing   (t17; I117, 217) of the bearing, which is solidly connected in rotation to. this mass of inertia. -   19. Torque transmission device according to any one of   Claims I to 18, characterized in that the inner ring (19   119; 219) of the bearing (16; 116; 216) is mounted on the sallie- (20), and the outer race (17; 117; 217) of the bearing is inserted into the central housing (18; 118; 218), and. carries the second mass of inertia (4) by   via the insulation (24; 125, 126; 225, 226. -30