Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
  • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
  • F16D3/64—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic elements arranged between substantially-radial walls of both coupling parts
  • F16D3/66—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic elements arranged between substantially-radial walls of both coupling parts the elements being metallic, e.g. in the form of coils
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
  • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
  • F16D2001/103—Quick-acting couplings in which the parts are connected by simply bringing them together axially the torque is transmitted via splined connections
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D2300/00—Special features for couplings or clutches
  • F16D2300/12—Mounting or assembling

Definitions

• Torque transmission assembly in particular for a motor vehicle
• the present invention relates to a torque transmission assembly, in particular for a motor vehicle and in particular the coupling in rotation of a double damping flywheel (DVA) to a double clutch.
• DVA double damping flywheel
• a double damping flywheel has a primary flywheel intended to be coupled in rotation to a driving shaft such as a crankshaft of an engine and a secondary flywheel intended to be coupled to a driven shaft such as a shaft input of a gearbox.
• a torsion damper is generally mounted between the primary and secondary flywheels for transmitting rotational torque between the flywheels by absorbing and damping vibrations and rotational acyclisms generated by the engine.
• a double clutch can alternately couple the motor shaft of a vehicle, usually via a double damping flywheel, with two coaxial input shafts of a gearbox, called robotic gearbox.
• the dual clutch allows to change gears while maintaining the transmission of engine torque to the wheels of the vehicle. Indeed, it usually comprises two clutches associated with odd and even gear ratios, respectively. During a gearshift, a first clutch is engaged while the second clutch is disengaged.
• Each clutch comprises a mechanism comprising an annular diaphragm for cooperating with a pressure plate integral in rotation with a clutch cover and the motor shaft.
• Each diaphragm is movable, by means of a control stop, between a rest position and an active position.
• the active position of the diaphragm corresponds to a coupling or decoupling of the engine shafts and gearbox and the diaphragm rest position corresponds to a decoupling or coupling of these motor shafts and gearbox.
• Each pressure plate urged by the corresponding diaphragm, is intended to clamp a friction disc on a corresponding reaction plate.
• Each friction disk is rotatably connected to a corresponding gearbox shaft and each reaction plate is rotatably connected to the clutch cover and a flywheel connected to the drive shaft.
• the document FR 2 860 845 discloses the structure and operation of a double clutch.
• the web of the double damping flywheel has splines engaged with play in complementary grooves of the connecting plate.
• An annular clearance-adjusting element is displaceably mounted on the annular web, between a first position in which it exerts no stress on the splines (inactive position) and a second position in which it forces the splines of the connecting plate against the splines of the annular web (active position).
• the play-catching element further includes tabs formed integrally therewith and serving to lock the play-catching element in its first position prior to its operation. More specifically, the tongues are deformable between a locking position in which their free ends abut against splines of the web, and an unlocking position in which they are no longer in abutment against the web.
• Such a set is also difficult to reboot after use.
• the object of the invention is in particular to avoid these disadvantages in a simple, efficient and economical way.
• a torque transmission assembly in particular for a motor vehicle, comprising a driving member comprising grooves engaged with clearance in complementary grooves of a driven member, a play catching element mounted movable on the driven member or on the driving member, between a first position in which it exerts no stress on the splines and a second position in which it forces the grooves of one of said members against the grooves of the other member, resilient biasing means biasing the play-catching member to its second position, and locking means of the play-catching member in its first position prior to its operation, characterized in that the locking means comprise means for blocking the elastic return means in an inactive position, these locking means or the elastic return means being biased s to a release position of the elastic return means during operation of the torque transmission assembly.
• the assembly according to the invention is applicable in particular to the coupling of a double damping flywheel and a clutch but can also be used for the coupling of other elements of a motor vehicle transmission.
• the locking means act directly on the elastic return means.
• the locking means can in fact retain the elastic return means in an inactive position or, on the contrary, release them so that they cause the displacement of the play catch-up element.
• the elastic return means are intended to be supported by their ends on the play catching element and on the driven or driving member, the locking means holding one of the ends of the elastic return means and maintaining it at distance from the play-catching member or the driving or driven member, respectively, prior to the operation of the torque transmission assembly.
• the torque transmission can take place in two opposite directions of rotation, respectively in a direct direction, corresponding to the driving direction of the member driven by the driving member, and in an opposite direction of rotation, said retro direction, the invention proposes that the locking means are biased towards a release position of the elastic return means by a rotation in the retro direction.
• the rotation of the bodies led and leading in the retro direction can in particular occur when the gearbox is in neutral or the clutch is in the disengaged position and the engine exerts a braking torque, called engine braking.
• a Rotation in the retro direction can also occur if the direction of rotation of the motor is reversed.
• the locking means comprise a hook carried by the play catching element and retaining one end of the elastic return means before operation, said hook being retractable in the release position of the elastic means of recall during operation of the torque transmission assembly.
• the hook can be pivotally mounted on the play catch element and can be biased towards its release position of the elastic return means by a finger carried by the driving member or conducted in operation.
• each hook is carried by the play catching element and retains one end of the elastic return means before operation, said hook being retractable in the release position of the elastic return means during operation of the transmission assembly of couple.
• the locking means comprise an elastic tongue whose one end is attached to the play catch element and a second end is free, the tongue being elastically deformable between a mounting position in which its second end retains the elastic return means in the inactive position and an operating position in which the tongue releases the elastic return means.
• the driving or driven member acts on the elastic return means and releases the elastic tongue which passes into its operating position.
• one end of the elastic return means in the inactive position, is engaged in a notch of the driving or driven member, or of the play catching element, and is released from said notch in operation.
• the notch can be arranged in different rooms, the essential point being that, after release, the elastic return means exert a force between one of the members led or leading, on the one hand, and the play catch-up element on the other hand, and that, before release, these elastic means do not move the play catching element to its second position.
• one end of the elastic return means bears against the driving or driven member, another end of the resilient biasing means being engaged in a notch of the driving member or respectively led in the mounting position.
• the play catching element is pressed on said other end so as to release it from the notch.
• said other end of the elastic return means may carry a cup comprising a frustoconical recess, the play catching element comprising a finger inserted into the recess during operation and cooperating with the frustoconical surface of the recess. in order to move the cup away from the stop formed by the notch.
• the driving member is part of a double damping flywheel and the driven member is a part of a clutch, including a double clutch.
• FIG. 1 is a partial view, from the front, of a transmission assembly according to a first embodiment of the invention
• - Figures 2 and 3 are partial views, from the rear, of the assembly of Figure 1, respectively before and after release of the elastic return means;
• FIG. 4 is a perspective view of a transmission assembly according to a second embodiment of the invention.
• FIG. 5 is a detail view of part of the assembly of FIG. 4;
• FIG. 6 and 7 are detail views of a third embodiment, respectively before and after release of the elastic return means
• FIGS. 8 and 9 are perspective views of a fourth embodiment, respectively before and after release of the elastic return means
• FIG. 10 is a perspective view and detail of a fifth embodiment, in the locking position of the elastic return means
• FIGS. 1 1 and 12 are detail views of a sixth embodiment, respectively before and after release of the elastic return means;
• FIG. 13 is a detail view in perspective of a seventh embodiment, in the locking position of the elastic return means.
• FIGS. 1 to 3 A first embodiment of a torque transmission assembly is illustrated in FIGS. 1 to 3.
• This assembly comprises a driving member, formed for example by a part 1 attached to an annular web of a double damping flywheel of a vehicle. automobile (or monoblock with the sail), and a driven member, formed for example by a connecting plate 2 to a double clutch.
• the driving member is only shown in FIG. He is no longer represented in the other figures.
• the connecting plate 2 comprises two annular parts 3, 4 fixed to one another by rivets 5.
• the first part 3 comprises radial tabs 6, intended to be fixed to a cover of the double clutch.
• the second part 4, fixed on the front face of the first part 3, comprises grooves 9 at its radially inner periphery as well as openings 10 (FIG. 1) at which support lugs 11 are formed by cutting and by folding.
• the free ends of the lugs 1 1 extending axially rearward, and are located in the axial plane of the first portion 3. These free ends are intended to form supports for the springs 8, as described in what follows.
• These lugs 1 1 also have a cam surface 12 oblique to the circumference, turned radially outwards ( Figure 3).
• An annular play-catching element 13 is mounted on the rear face of the first part 3 of the connecting plate 2, by means of rivets 14 mounted in oblong openings 15 of the play-catching element 13.
• the oblong openings 15, in the shape of an arc of a circle allow an angular displacement of the play-catching element 13 with respect to the connection plate 2, of a value of between 0.3 and 1 °, preferably of the order of 0.8 °.
• the radially inner periphery of the play-catching element 13 comprises zones equipped with splines 16 similar to those of the splines 9 of the second part 4 of the connection plate 2.
• the ends and the bases of the splines 16 are however narrower than those of flutes 9.
• the play-catching element 13 furthermore comprises windows 17 of the connection plate 2 and serving to hold the springs 8. More particularly, the edges of the windows situated on the right in FIG. 2 are provided with abutments 18 for support. springs 8. Guides 41 also extend inside the springs from the abutments 18.
• Hooks 19 (FIG. 2) are pivotally mounted on the rear face of the play-catching element 13, around rivets 20.
• the hooks 19 each comprise a front end 21 for locking the springs 8 and a tapered rear end 22, the rivet 20 forming the pivot axis being located in the middle portion of the hook 19.
• the end (22) is dimensioned so as to position the center of gravity substantially to the right of the axis of rotation, so as to ensure the maintenance the correct positioning of the hook during manufacture, and especially during test phases.
• the driving member 1 comprises splines 24 at its radially outer periphery, cooperating with the splines of the connecting plate 2.
• the grooves 9 and 24 are mounted with clearance in each other.
• This clearance allows a relative rotation of the annular web (or driving member 1) relative to the connecting plate (or driven member 2), the angular displacement between these two members 1, 2 is greater than the angular displacement between the element 13 and the connecting plate 2.
• the driving member 1 further comprises tabs 42 projecting radially inwards, for mounting on the annular web of the double damping flywheel.
• this assembly is not limited to the coupling of a double damping flywheel and a clutch. It can also be used to couple other elements of a transmission of a motor vehicle.
• the torque can be transmitted in two opposite directions of rotation, respectively in a direct direction (arrow D in FIG. 1), corresponding to the driving direction of the driven member 2 by the driving member 1, and in an opposite direction of rotation, said retro direction (arrow R in Figure 1).
• the rotation of the leading members 1 and led 2 in the retro direction R may in particular occur when the gearbox is in neutral or the clutch is in the disengaged position and the engine exerts a braking torque, called engine braking.
• a rotation in the retro direction can also occur if the direction of rotation of the motor is reversed.
• the play catching element 13 is in the inactive position: it applies no effort on the grooves 9, 24 of said bodies.
• a transmission assembly according to a second embodiment is illustrated in Figures 4 and 5. This differs from the previous embodiment in that the connecting plate 2 has neither opening nor tab.
• the pivoting of the hook 19 is obtained by pressing the end 21 thereof on a pad 43 made of material with the connecting plate 2, for example obtained by extrusion.
• the rear end 22 of the hook 19 further comprises a stop 44 bent axially and housed in a slot 45 of the play catching member 13. This stop 44 is intended to bear against the edge of the light 45 when the hook 19 is in the release position of the spring 8, as can be seen in FIG.
• FIGs 6 and 7 Another embodiment is shown in Figures 6 and 7. This embodiment differs from that of Figures 1 to 3 in that the hooks 19 are not pivotally mounted about axes, but are connected to the catch-up element play 13 by elastically deformable tabs 28 fixed by means of rivets 20.
• the cam surfaces 12 of the tabs 1 1 come to spread the front ends 21 of the hooks 19 by deformation of the tabs 28 (FIG. 7).
• the springs 8 push back the play catching element 13 which pivots with respect to the driven member 2 so as to make up the clearance between the splines 24 of the driving member 1 (not shown) and those 9 of the driven member 2.
• FIGS. 8 and 9 illustrate a fourth embodiment in which the play-catching element 13 comprises elastic locking tabs 29 extending circumferentially.
• These tongues 29 comprise first ends 30 connected to the rest of the play catching element 13 and second locking ends 31 intended to form stops for the second ends 26 of the springs 8 before release.
• the constrained position of the tongues 29 is the locking position shown in FIG. 8, in which the tongue 29 is spaced apart from the plane of the play-catching element 13.
• the rest position of the tongue 29 is the unlocking position represented by FIG. in FIG. 9, in which the tongue 29 extends in the plane of the play-catching element 13.
• the play catching element 13 further comprises lugs 32 intended to bear against some of the grooves 24 of the driving member 1 (not shown). These tabs 32 have bearing surfaces inclined relative to the radial plane so as to conform to the inclined surfaces of the grooves 24 of the driving member 1.
• the springs 8 are held in position by curved legs
• the driven member 2 comprises windows in which the springs 8 are housed.
• the edges 35 of the windows opposite the tabs 34 of the play-catching element 13 are intended to bear against the second ends 26 of the springs 8.
• the tongues 29 are maintained in their position constrained by the springs 8. More particularly, the free ends 31 of the tongues 29 are jammed by the second ends 26 of the springs 8.
• the play catching element 13 exerts no effort on the grooves 9, 24 of the driven member 2 or the driving member 1 (inactive position).
• the springs 8 then force the play-catching element 13 into its active position, in which it plates the splines 24 of the driving member 1 against those 9 of the driven member 2 so as to catch the mounting clearance between these splines.
• FIG. 10 illustrates a fifth embodiment, similar to that of FIGS. 8 and 9, in which the deformable tongue 29 is not formed in one piece with the play catch-up element, but consists of a separate piece attached to the play catching element 13.
• FIGS. 1-10 A sixth embodiment is shown in FIGS.
• fingers 38 of the play-catching element 13 compress the springs 8 by pressing on their second end 26, and thus release the second ends 26 of the springs 8 out of the springs. notches 37, so that they exert a force on the play catching element 13 (active position).
• the shapes of the fingers 38 and the notches 37 are adapted to operate a clearance of the springs 8 out of the notches 37 during the compression of the springs 8 by the fingers 38.
• FIG. 13 illustrates a seventh embodiment similar to that shown in FIGS. 11 and 12. However, this difference differs in that the second ends 26 of the springs 8 carry cups 39 each comprising a frustoconical recess 40.
• the play catching element 13 comprises fingers 38 inserted into the recesses 40 during operation in the retro direction R and cooperating with the frustoconical surfaces of the recesses 40 so as to disengage the cup 39 from the notch 37.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Mechanical Operated Clutches (AREA)
• Motor Power Transmission Devices (AREA)

Applications Claiming Priority (2)

Publications (1)

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ID=47263481

Family Applications (1)

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• 2011
  • 2011-11-08 FR FR1160161A patent/FR2982332B1/fr active Active
• 2012
  • 2012-11-06 KR KR1020147011780A patent/KR102001270B1/ko active IP Right Grant
  • 2012-11-06 WO PCT/FR2012/052562 patent/WO2013068689A1/fr active Application Filing
  • 2012-11-06 EP EP12794447.8A patent/EP2776728A1/fr not_active Withdrawn
  • 2012-11-06 CN CN201280054794.9A patent/CN103930686B/zh active Active

Non-Patent Citations (2)

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