WO2009034274A1 - Dispositif d'embrayage a friction equipe d'un double volant amortisseur comportant des moyens pour limiter les deplacements radiaux du voile par rapport au volant primaire - Google Patents
Dispositif d'embrayage a friction equipe d'un double volant amortisseur comportant des moyens pour limiter les deplacements radiaux du voile par rapport au volant primaire Download PDFInfo
- Publication number
- WO2009034274A1 WO2009034274A1 PCT/FR2008/051444 FR2008051444W WO2009034274A1 WO 2009034274 A1 WO2009034274 A1 WO 2009034274A1 FR 2008051444 W FR2008051444 W FR 2008051444W WO 2009034274 A1 WO2009034274 A1 WO 2009034274A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- abutment face
- secondary web
- primary assembly
- radially
- web
- Prior art date
Links
Classifications
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- 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
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
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- 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
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
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- 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
- F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
- F16D3/04—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow radial displacement, e.g. Oldham couplings
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- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
- F16F15/13164—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses characterised by the supporting arrangement of the damper unit
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- 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
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
- F16D2013/703—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members the pressure plate on the flywheel side is combined with a damper
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- 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
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
- F16D2021/0607—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate
- F16D2021/0615—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate the central input plate is supported by bearings in-between the two clutches
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- 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
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
- F16D2021/0692—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric with two clutches arranged axially without radial overlap
Definitions
- the invention relates to a friction clutch device, particularly for a motor vehicle, for coupling a first rear motor shaft and a second driven shaft before, a free front end section of the first motor shaft being free to wrestle radially with respect to a free rear end section of the second driven shaft.
- the invention relates more particularly to a friction clutch device, in particular for a motor vehicle, for coupling a first rear motor shaft and at least one second driven front shaft, a free front end section of the first motor shaft being free to wrestle radially with respect to a free rear end section of the second driven shaft, the clutch device comprising:
- a rear primary assembly which is carried by the front end section of the drive shaft and which is rotatably connected to the drive shaft;
- a front radial secondary web which is rotatably connected to a reaction plate of the clutch device and which is carried by the rear end section of the driven shaft;
- At least one circumferentially acting elastic member which is arranged in the radially inner bottom of a peripheral housing of the primary assembly and which is interposed circumferentially between a bearing face of the primary assembly and a tab of the secondary web for Rotary link with angular deflection the secondary veil with the primary assembly.
- the secondary web of the double damping flywheel causes the clutch to enter through a rotating connection.
- the transmission of the torque by this connection implies that the secondary web is secured radially to the driven shaft.
- the primary assembly When the engine is in operation, the primary assembly is able to move radially, independently of the driven shaft, particularly because of the crankshaft bending caused by the explosions in the cylinders.
- the balancing in rotation of the primary assembly is never perfect, and the motor shaft is likely to be bent radially, independently of the driven shaft, under the effect of unbalance of the primary assembly during its rotation.
- the driven shaft carries a portion of the clutch, including a reaction plate, which is also free from defect balancing. During its rotation, the driven shaft is also likely to bend radially, regardless of the motor shaft, because of unbalance clutch elements.
- This radial deflection of the driven shaft can also be due to misalignments or deformations during transmission of the engine torque.
- the invention proposes a device of the type described above, characterized in that the secondary web carries a first axial abutment face which is arranged with a radially radial clearance vis-à-vis a second axial end face of the cover so as to limit the radial displacements of the secondary web relative to the primary assembly so that the tab of the secondary web does not touch the bottom of the housing of the primary assembly when the front end section the motor shaft is depressed radially with respect to the rear end of the driven shaft.
- the first abutment face of the secondary web is arranged radially inward relative to the bottom of the housing;
- the first abutment face of the secondary web is arranged radially to the right of the tab of the secondary web;
- the second abutment face of the primary assembly extends over an angular sector covering at least the angular displacement of the first abutment face of the secondary veil;
- the second abutment face of the primary assembly is annular
- the first abutment face of the secondary web extends over an annular contour coaxial with the axis;
- the first abutment face is carried by lugs which are evenly distributed along the annular contour
- the first abutment face is formed by an annular bearing surface of the secondary veil
- One of the first or second abutment faces is carried by an annular ring which is arranged radially vis-à-vis the other abutment face;
- the ring is made of material with a friction washer which is interposed axially between the secondary web and the primary assembly;
- the ring is linked in rotation with the secondary veil
- the ring is linked in rotation with the primary assembly; -
- the first abutment face of the secondary web is directed radially outwardly and the second abutment face of the primary assembly is directed radially inwardly;
- the housing is delimited axially towards the front by an annular cover which is fixed to a rear primary flywheel of the primary assembly, and in that the second abutment face of the primary assembly is formed by the annular inner peripheral edge. of the lid.
- FIG. 1 is a half-view in axial section along the sectional plane 1-1 of Figure 5 which shows a friction clutch device comprising a double damping flywheel made according to the teachings of the invention;
- FIG. 2 is an exploded perspective view showing the double damping flywheel of the clutch device of FIG. 1;
- FIG. 3 is a front view which shows the double damping flywheel of Figure 2 mounted without its cover;
- Figure 4 is a view similar to that of Figure 1 according to the sectional plane 4-4 of Figure 5;
- FIG. 5 is a front view which shows the double damping flywheel of Figure 3 with its primary cover
- Figure 6 is a view similar to that of Figure 1 which shows the friction clutch device comprising a double damping flywheel made according to a second embodiment of the invention.
- FIG. 1 shows a clutch device 10 which is intended to couple a motor shaft which is arranged axially towards the rear and of which a free front end section 12 is shown on the left in FIG. less a driven shaft 14 which is arranged forward.
- the drive shaft 12 is rotatable about an axis of rotation "B" and is rotated by a motor (not shown) of the motor vehicle.
- the clutch device shown in Figure 1 comprises two driven shafts whose free end sections 14A, 14B are shown.
- the driven shafts 14A, 14B are rotatably mounted substantially coaxially with the drive shaft 12.
- the first driven shaft 14A forms an axial tube inside which is arranged the second driven shaft 14B.
- Each of the driven shafts 14A, 14B is rotatable independently of the other.
- the free front end 16 of the drive shaft 12 is arranged axially behind and away from the free rear ends 18A, 18B of the driven shafts 14A, 14B.
- the driven shafts 14A, 14B are connected to a rear gearbox (not shown). More particularly; the first driven shaft corresponds to certain transmission speed ratios, for example the odd-speed ratios, while the second shaft corresponds to the other gear ratios, for example the even gear ratios.
- the clutch device 10 comprises first temporary coupling means of the first driven shaft 14A with the drive shaft 12 which are carried only by the first driven shaft 14A.
- the clutch device 10 comprises a circular radial reaction plate 20 which is rotatably mounted about the axis of rotation "B".
- the reaction plate 20 is carried by the rear end section of the first driven shaft 14A via a ball bearing 22.
- the reaction plate 20 is more particularly mounted axially fixed relative to the rear end section of the first driven shaft 14A.
- reaction plate 20 is integral in rotation with the drive shaft 12 via a double damping flywheel 24 which is arranged at a rear end of the clutch device and which will be described in more detail by the after.
- the first coupling means also comprise a first pressure annular front plate 26 which is mounted to rotate with the reaction plate 20 about the axis of rotation "B" and is slidably mounted axially relative to the reaction plate 20
- the first pressure plate 26 is more particularly arranged axially vis-à-vis a front face 28 of the reaction plate 20.
- a first coaxial disk 30 before friction is interposed axially between the reaction plate 20 and the front pressure plate 26.
- the front friction disc 30 has on both sides an annular friction lining.
- the friction front disc 30 is mounted to rotate with the first driven shaft 14A, and is axially slidably mounted on the first driven shaft 14A.
- the friction front disc 30 is intended to be clamped against the front face 28 of the reaction plate 20 by the first pressure plate 26 to temporarily couple the first driven shaft 14A with the motor shaft 12.
- the clutch device 10 also comprises second temporary coupling means of the second driven shaft 14B with the drive shaft 12 which are arranged symmetrically with the first coupling means with respect to the reaction plate 20 and which are carried only by the led shafts 14A, 14B.
- the second coupling means thus comprise a rear pressure plate 32 and a rear friction disc 34 for the temporary coupling of the second driven shaft 14B with the drive shaft 12.
- the functions of the rear pressure plate 32, respectively of the rear friction disc 34 are similar to those of the front pressure plate 26, respectively of the front friction disc 30 .
- the rear pressure plate 32 is mounted axially vis-à-vis the rear face 36 of the reaction plate.
- the rear pressure plate 32 is rotatably connected to the reaction plate 20 and slides axially with respect to the reaction plate 20.
- the rear friction disk 34 is mounted to rotate with the second driven shaft 14B, and is axially slidably mounted on the second driven shaft 14B.
- the rear friction disk 34 is intended to be clamped against the rear face 36 of the reaction plate 20 by the rear pressure plate 32 to temporarily couple the second driven shaft 14B with the motor shaft 12.
- the dual flywheel 24 more particularly comprises an input element of the engine torque which is here formed by a rear primary assembly 38 and an output element of the engine torque which is here formed by a secondary web 40 before.
- the primary assembly 38 comprises a rear primary flywheel 41 which extends radially coaxially with the axis of rotation "B".
- the primary assembly 38 is carried by the front end section of the drive shaft 12 and is rotatably connected to the drive shaft 12 without radial clearance and without angular movement about the axis "B".
- a front end fixing flange 42 of the drive shaft 12 is fixed against a rear end face of a hub 44 of the primary flywheel 41 of the primary assembly 38 via a plurality of screws 46.
- the primary assembly 38 is thus integral with the movements of the motor shaft 12 in all directions, and in particular radially.
- the primary assembly 38 also carries a starter gear ring 48 which is arranged around an outer peripheral axial face of the primary flywheel 41 of the primary assembly 38.
- the primary assembly 38 has at its outer periphery a skirt 50 which extends axially forwardly from an outer peripheral edge of the primary flywheel 41.
- the secondary web 40 forms a ring which extends radially about the axis of rotation "B".
- the secondary web is more particularly arranged radially forward and at a distance from a radial face 52 before the primary assembly 38.
- the secondary web 40 has an outer peripheral diameter which is smaller than the diameter of the primary flywheel 41 so as to provide a radial housing 60 between the outer peripheral edge of the secondary web 40 and the inner peripheral face 58 of the skirt 50 as will be described by the following.
- the secondary web 40 is rotatably connected to the reaction plate 20 of the clutch device 10, and is carried only by the first driven shaft 14A.
- the secondary web 40 is rotatably supported by the rear pressure plate 32 which is itself carried by the rear end section of the first driven shaft 14A through of the reaction plate 20.
- the inner peripheral edge 51 of the secondary web 40 has radial teeth which are received in axial sliding in axial grooves of a hub 54 which extends axially rearwards from a rear face of rear pressure plate 32.
- the secondary web 40 is rotatably connected with the primary assembly 38 with damped angular displacement.
- At least one elastic member 56 with circumferential action 56 is arranged against the bottom 58 radially inside a peripheral housing 60 of the primary assembly 38.
- the elastic member 56 is interposed circumferentially between a support 62 of the primary assembly 38 and a support lug 64 of the secondary web 40.
- the double damping flywheel 24 more particularly comprises two elastic members 56 which are arranged symmetrically with respect to a diameter of the primary flywheel 41.
- the arrangement of only one of these elastic members will therefore be described later, the description being applicable by symmetry to the other elastic member.
- the elastic member 56 is more particularly formed by a helical spring which extends circumferentially in an arc of a circle for example over an angular sector of about 150 °.
- the spring 56 is arranged against the radially inner axial face 58 of the peripheral skirt 50 of the primary assembly 38 which forms the bottom of the housing 60.
- the housing 60 is closed axially towards the rear by the primary flywheel 41 of the assembly primary 38 and axially forwardly by a radial annular cover 66 of the primary assembly 38 which is attached to a leading end edge of the skirt 50.
- the radial displacements of the spring 56 are limited outwards by the skirt 50 and inwardly by an axial constriction formed by curves 68 of the primary flywheel 41 of the primary assembly 38 and the cover 66.
- the cover 66 comprises an inner end annular section 70 which is arranged vis-à-vis a front face of the primary flywheel 41 of the primary assembly 38 at an axial distance less than the axial width of the spring 56 to form the strangulation.
- an outer annular portion 78 of the secondary web 40 is interposed axially in the constriction between the primary assembly 38 and an inner annular portion 80 of the lid 66. More particularly, the diameter of the outer peripheral edge of the web 40 is greater than the diameter. inner device of the lid 66.
- a guide chute 72 is interposed radially between the spring 56 and the bottom 58 of the housing 60 to favor the circumferential displacements of its turns when the spring 56 is pressed against the bottom 58 of the housing 60 by the centrifugal force.
- the chute has the same circumferential length as the spring 56 when the clutch device is at rest.
- the housing 60 is delimited circumferentially by a first axial axial bearing face 62 and by a second radial axial bearing face 62.
- the front face 52 of the primary flywheel 41 of the primary assembly 38 and the rear face of the cover 66 each comprise two bosses 74 diametrically opposed. The lateral faces of the bosses thus form the radial bearing faces 62 which delimit the two housings 60.
- the bosses 74 of the cover 66 are arranged axially in facing relation with the bosses 74 of the primary flywheel 41.
- the secondary web 40 comprises two tabs 64 which extend radially from the outer peripheral edge of the web to a free outer end 77.
- the tab 64 which is arranged axially between two concordant bosses of the primary flywheel 41 and the cover 66 as shown in Figure 4.
- Each tab 64 is delimited circumferentially by two lateral radial edges 76 which are intended to come into contact with the end opposite the spring 56 to urge the springs 56 in one direction or the other.
- Each tab 64 occupies an angular sector substantially identical to that of the bosses 74, as shown in FIG.
- the secondary web 40 is thus capable of pivoting in both directions relative to the primary assembly 38, for example more or less 60 °, by biasing the springs 56 by means of the tabs 64.
- the springs 56 are then compressed by bearing on the corresponding bearing faces 62 of the bosses 74.
- the tabs 64 are received with an axial clearance "J1" with respect to the front face 52 of the primary assembly 38 and relative to the cover 66, as illustrated in Figure 4.
- the tabs 64 are also received with a radial clearance "J2" between their outer end edge 77 and the inner face 58 of the skirt 50, as shown in FIG. 4. More particularly, this radial clearance "J2" is greater than the radial thickness of the guiding chutes 72 of the springs 56.
- a first radial front radial washer 82A is interposed between the front face of the outer section 78 of the secondary web 40 and the rear face of the inner section 80 of the cover 66, and a second rear radial washer 82B of friction is interposed between the rear face of the outer section 78 of the secondary web 40 and the face before 52 of the primary flywheel 41.
- friction washers 82A, 82B are also sometimes called “hysteresis washers”.
- a spring washer 84 of the "Belleville” type is interposed axially under tension between the front washer 82A and the cover 66 to axially push the web 40 and the friction washers 82A, 82B against the primary flywheel 41 of the primary assembly 38, bearing on the cover 66, as shown in FIGS. 1 and 4.
- the web 40 is susceptible to damage.
- disturbances in operation are likely to occur, in particular the tabs 64 may be blocked against one of the circumferential ends of the troughs 72, thus causing angular locking without damping the secondary web 40 with respect to the assembly. primary 38.
- the invention proposes that the secondary web 40 carries a first stop face 86 which is arranged with a radial clearance "J3" radially opposite a second abutment face 88 of the cover 66. so as to limit the radial displacements of the secondary flywheel relative to the primary assembly 38.
- the outer end 77 of the tab 64 of the secondary web 40 does not touch the bottom 58 of the housing 60 of the primary assembly 38 when the front end section of the drive shaft 12 moves radially with respect to the rear end of the first driven shaft 14A.
- the radial clearance "J3" between the two abutment faces 86, 88 is smaller than the radial clearance "J2" between the outer end 77 of the tabs 64 and the bottom 58 of the housing 60.
- the bottom of the housing 60 is formed by an inner face of the chute 72.
- the radial clearance "J3" is then designed so that the outer end 77 of the legs 64 do not touch not the guiding chute 72 forming here the bottom of the housing 60.
- the first abutment face 86 of the web extends at least over an angular sector coinciding with the angular sector on which the tab 64 of the web 40 extends.
- the first stop face 86 of the web is arranged radially to the right of the leg 64.
- the first abutment face 86 of the web 40 is advantageously arranged radially inwardly relative to the bottom 77 of the housings 60.
- the first abutment face 86 of the web 40 is arranged at a radial distance from the axis "B" which is less than the radial distance from the free outer end 77 of the tabs 64 relative to the axis "B".
- the first abutment face 86 of the web 40 is formed by an outer peripheral axial face 86 of a ring 90 which is arranged without radial clearance around a radially outer bearing surface 92 extending axially forward from an inner edge of the outer section 78 of the web 40.
- the first abutment face 86 thus extends axially forwardly from the front face of the web 40.
- the bearing 92 has a smaller outer diameter than the inner peripheral diameter of the cover 66.
- the bearing surface 92 is thus arranged radially opposite an axial inner peripheral edge of the cover 66 which advantageously forms the second axial abutment face 88 of FIG. the primary assembly 38.
- the first abutment face 86 of the web 40 is directed radially outwards and the second abutment face 88 associated with the primary assembly 38 is directed radially inwards.
- the first abutment face 86 of the web 40 thus has an annular shape coaxial with the axis "B" which allows a regular distribution of the masses around the axis "B” in order to avoid forming unbalances, and which makes it possible to in addition to limiting radial movements in all directions.
- the ring 90 is advantageously made integrally with the front washer 82A friction.
- the ring 90 thus forms a flange which extends axially forwardly from an inner end edge of the front friction washer 82A so as to have an axial "L" shaped section.
- the ring 90 is moreover immobilized in rotation with respect to the cover 66.
- the inner peripheral edge 88 of the cover 60 includes regularly distributed indentations 94 which are intended to receive counterparts 96 arranged in the angle formed by the ring 90. and the front friction washer 82A.
- the ring 90 is here mounted without radial clearance on the bearing 92 of the web 40, and its outer face 86 is arranged with the radial clearance "J3" relative to the inner peripheral edge 88 of the cover 66. even, the counterparts 96 of the ring 90 are received with the same radial clearance "J3" in the indentations 94.
- the ring 90 is advantageously made of a material sliding to form a rolling bearing.
- the ring 90 is mounted without radial clearance with respect to the cover 66.
- the second abutment face 88 of the primary assembly 38 is then formed by the inner peripheral face of the ring 90, while that the first abutment face 86 of the web 40 is formed by the shoulder 92.
- the radial clearance "J3" is then reserved between the inner peripheral face of the ring 90 and the outer peripheral face of the span 92.
- the ring 90 is mounted to rotate with the web 40, for example via axial pins of the washer which are received in associated holes of the web 40.
- the first abutment face 86 of the web 40 is formed directly by the bearing surface 92 of the web 40.
- the radial clearance "J3" is then reserved between the bearing 92 of the web 40 and the inner peripheral edge 88 of the lid 66.
- the first abutment face 86 of the web 40 is carried by lugs 98 which extend axially forwards from a front face of the web 40.
- the outer face of the lugs form the first stop face 86 of the web 40.
- the lugs 98 are for example made by cuts of the web 40 which are then folded.
- the lugs 98 are thus arranged at least radially to the right of the lugs 64 of the web 40.
- the pins 98 are here arranged regularly on an annular contour coaxial with the axis "B" which is arranged radially inward with respect to the inner peripheral edge 88 of the cover 66.
- the regular distribution of the lugs 98 around the axis "B" avoids the formation of unbalance in the web 40.
- annular abutment face is thus discontinuous and formed by the meeting by outer faces 86 of the lugs 98 which are evenly distributed along the abutment contour.
- the second abutment face 88 of the primary assembly 38 is formed by the radially outer edge in a circular arc coaxial with the axis "B" of an associated window which is made either in the cover 66, or in the primary flywheel 41.
- the lugs 98 which thus extend axially either towards the front or towards the rear, are thus inserted axially in a window which extends for this purpose on a angular sector covering at least the angular deflection of the first abutment face of the veil.
- the second abutment face of the primary assembly 38 may be formed directly by an outer edge or inner arcuate of a window of the primary flywheel of the primary assembly.
- the invention is also applicable to other types of friction clutch, for example monodisc or multi-disc, in which the reaction plate and the web are guided solely by the driven shaft and are free radially relative to the motor shaft.
- the invention also applies to locking clutches for a hydrokinetic coupling device comprising a torque converter.
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112008002471.5T DE112008002471B4 (de) | 2007-09-11 | 2008-07-31 | Reibungskupplungsvorrichtung mit einem Doppeldämpfungsschwungrad mit Mitteln zum Begrenzen von radialen Bewegungen der Flanschscheibe relativ zum Primärschwungrad |
JP2010524546A JP2010539404A (ja) | 2007-09-11 | 2008-07-31 | ウエブの第1のホイールに対する径方向の運動を制限するための手段を有する複式減衰ホイールを備えた摩擦クラッチ装置 |
HU1000316A HUP1000316A2 (en) | 2007-09-11 | 2008-07-31 | Friction clutch device provided with a dual damping wheel including means for limiting the radial movements of the web relative to the primary wheel |
KR1020107007831A KR101514102B1 (ko) | 2007-09-11 | 2008-07-31 | 1차 휠에 대한 웨브의 반경방향 이동을 제한하기 위한 수단을 포함하는 듀얼 댐핑 휠이 마련되어 있는 마찰 클러치 장치 |
CN2008801125844A CN101861471B (zh) | 2007-09-11 | 2008-07-31 | 包括用于限制副片体相对于主飞轮的径向移动的部件、配有双减振飞轮的摩擦离合器装置 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR0757500A FR2920845B1 (fr) | 2007-09-11 | 2007-09-11 | Dispositif d'embrayage a friction equipe d'un double volant amortisseur comportant des moyens pour limiter les deplacements radiaux du voile par rapport au volant primaire |
FR0757500 | 2007-09-11 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2009034274A1 true WO2009034274A1 (fr) | 2009-03-19 |
Family
ID=39232828
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR2008/051444 WO2009034274A1 (fr) | 2007-09-11 | 2008-07-31 | Dispositif d'embrayage a friction equipe d'un double volant amortisseur comportant des moyens pour limiter les deplacements radiaux du voile par rapport au volant primaire |
Country Status (7)
Country | Link |
---|---|
JP (1) | JP2010539404A (fr) |
KR (1) | KR101514102B1 (fr) |
CN (1) | CN101861471B (fr) |
DE (1) | DE112008002471B4 (fr) |
FR (1) | FR2920845B1 (fr) |
HU (1) | HUP1000316A2 (fr) |
WO (1) | WO2009034274A1 (fr) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019053267A1 (fr) * | 2017-09-18 | 2019-03-21 | Valeo Embrayages | Dispositif de transmission de couple, amortisseur de torsion et assemblage associe |
FR3090774A1 (fr) * | 2018-12-20 | 2020-06-26 | Valeo Embrayages | Dispositif de transmission pour véhicule automobile |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010022916A1 (de) * | 2009-06-29 | 2010-12-30 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Drehmomentübertragungseinrichtung |
FR2956172B1 (fr) * | 2010-02-05 | 2015-07-03 | Renault Sas | Mecanisme d'embrayage sec pour boite de vitesses de vehicule automobile |
CN103221708B (zh) * | 2010-11-11 | 2016-03-09 | 舍弗勒技术股份两合公司 | 扭矩传递装置 |
DE102011086712A1 (de) * | 2010-12-09 | 2012-06-14 | Schaeffler Technologies Gmbh & Co. Kg | Drehmomentübertragungseinrichtung |
KR101541661B1 (ko) * | 2011-08-18 | 2015-08-03 | 주식회사평화발레오 | 건식 더블 클러치 |
DE102011082370A1 (de) * | 2011-09-08 | 2013-03-14 | Zf Friedrichshafen Ag | Drehschwingungsdämpferanordnung, insbesondere für den Antriebsstrang eines Fahrzeugs |
FR3009592B1 (fr) * | 2013-08-08 | 2015-07-31 | Valeo Embrayages | Dispositif d'embrayage a rattrapage d'usure, notamment pour vehicule automobile |
DE102016125263A1 (de) * | 2016-10-26 | 2018-04-26 | Schaeffler Technologies AG & Co. KG | Doppelkupplung mit abschnittsweise eintauchendem Drucktopf und Bausatz aus Doppelkupplung und Schwingrad |
FR3066003B1 (fr) * | 2017-05-03 | 2020-06-26 | Valeo Embrayages | Amortisseur de torsion, vehicule automobile et procede de montage associes |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2664340A1 (fr) * | 1990-07-07 | 1992-01-10 | Luk Lamellen & Kupplungsbau | Dispositif de transmission de couple. |
FR2778439A1 (fr) * | 1998-05-07 | 1999-11-12 | Mannesmann Sachs Ag | Amortisseur d'oscillation de torsion comprenant un element amortisseur situe du cote de l'organe d'entrainement |
FR2886996A1 (fr) * | 2005-06-14 | 2006-12-15 | Valeo Embrayages | Mecanisme d'embrayages multiples avec disque de friction en 2 parties |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
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DE10013576B4 (de) | 1999-03-26 | 2013-02-07 | Schaeffler Technologies AG & Co. KG | Kupplungsaggregat |
JP2006144883A (ja) | 2004-11-18 | 2006-06-08 | Exedy Corp | サブダンパーユニットおよびクラッチディスク組立体 |
FR2902166B1 (fr) | 2006-06-08 | 2008-07-25 | Valeo Embrayages | Double volant amortisseur, en particulier pour vehicule automobile |
-
2007
- 2007-09-11 FR FR0757500A patent/FR2920845B1/fr active Active
-
2008
- 2008-07-31 CN CN2008801125844A patent/CN101861471B/zh active Active
- 2008-07-31 KR KR1020107007831A patent/KR101514102B1/ko active IP Right Grant
- 2008-07-31 HU HU1000316A patent/HUP1000316A2/hu unknown
- 2008-07-31 WO PCT/FR2008/051444 patent/WO2009034274A1/fr active Application Filing
- 2008-07-31 JP JP2010524546A patent/JP2010539404A/ja active Pending
- 2008-07-31 DE DE112008002471.5T patent/DE112008002471B4/de active Active
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2664340A1 (fr) * | 1990-07-07 | 1992-01-10 | Luk Lamellen & Kupplungsbau | Dispositif de transmission de couple. |
FR2778439A1 (fr) * | 1998-05-07 | 1999-11-12 | Mannesmann Sachs Ag | Amortisseur d'oscillation de torsion comprenant un element amortisseur situe du cote de l'organe d'entrainement |
FR2886996A1 (fr) * | 2005-06-14 | 2006-12-15 | Valeo Embrayages | Mecanisme d'embrayages multiples avec disque de friction en 2 parties |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019053267A1 (fr) * | 2017-09-18 | 2019-03-21 | Valeo Embrayages | Dispositif de transmission de couple, amortisseur de torsion et assemblage associe |
FR3071291A1 (fr) * | 2017-09-18 | 2019-03-22 | Valeo Embrayages | Dispositif de transmission de couple, amortisseur de torsion et assemblage associe |
FR3090774A1 (fr) * | 2018-12-20 | 2020-06-26 | Valeo Embrayages | Dispositif de transmission pour véhicule automobile |
Also Published As
Publication number | Publication date |
---|---|
CN101861471A (zh) | 2010-10-13 |
KR20100081314A (ko) | 2010-07-14 |
DE112008002471B4 (de) | 2021-07-29 |
JP2010539404A (ja) | 2010-12-16 |
KR101514102B1 (ko) | 2015-04-21 |
CN101861471B (zh) | 2013-04-24 |
FR2920845B1 (fr) | 2010-03-12 |
DE112008002471T5 (de) | 2010-08-19 |
HUP1000316A2 (en) | 2010-11-29 |
FR2920845A1 (fr) | 2009-03-13 |
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