WO2015173086A1 - Mechanism for filtering torque fluctuations - Google Patents

Mechanism for filtering torque fluctuations Download PDF

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Publication number
WO2015173086A1
WO2015173086A1 PCT/EP2015/059943 EP2015059943W WO2015173086A1 WO 2015173086 A1 WO2015173086 A1 WO 2015173086A1 EP 2015059943 W EP2015059943 W EP 2015059943W WO 2015173086 A1 WO2015173086 A1 WO 2015173086A1
Authority
WO
WIPO (PCT)
Prior art keywords
oscillating
raceway
axis
flywheel
revolution
Prior art date
Application number
PCT/EP2015/059943
Other languages
French (fr)
Inventor
Roel Verhoog
Benoit FLECHE
Franck CAILLERET
Original Assignee
Valeo Embrayages
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Valeo Embrayages filed Critical Valeo Embrayages
Priority to DE112015002251.1T priority Critical patent/DE112015002251T5/en
Publication of WO2015173086A1 publication Critical patent/WO2015173086A1/en

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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
    • 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
    • F16F15/13128—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 the damping action being at least partially controlled by centrifugal masses
    • 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
    • F16F15/13157—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 with a kinematic mechanism or gear system, e.g. planetary
    • 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
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/1464—Masses connected to driveline by a kinematic mechanism or gear system
    • F16F15/1471—Masses connected to driveline by a kinematic mechanism or gear system with a kinematic mechanism, i.e. linkages, levers

Definitions

  • the invention relates to a mechanism for filtering the acyclisms of an internal combustion engine, located upstream of a gearbox, in particular for an application to a motor vehicle, including an integrated filtration mechanism to a torque converter or dry clutch mechanism.
  • the articulated modules oppose the relative rotation of the masses of inertia by exerting a return torque substantially proportional to the relative rotation of the two masses of inertia and to the square of the rotational speed of the mass of inertia. inertia linked to the crankshaft.
  • this device is particularly sensitive to hysteresis phenomena generated in particular by the pivots of the articulated connection modules.
  • a torque fluctuation filtration mechanism which may be intended to be interposed between a crankshaft of an internal combustion engine rotating about an axis of revolution and a gearbox, and having a damping member rotating about the axis of revolution, an oscillating flywheel rotating about the axis of revolution relative to the member to be damped, and at least one connecting module allowing an angular displacement of the flywheel oscillating relative to the member to be damped on either side of a reference position, the connecting module comprising at least one oscillating arm pivoting radially relative to the member for damping and a rolling body rolling connection on a raceway formed on the swing arm and on a raceway formed on the oscillating flywheel.
  • the member to be damped is thus biased by counter-couples which compensate themselves at least partially, namely on the one hand an acyclic input torque, for example coming from an internal combustion engine, and on the other hand an oscillating torque entering through the articulation of each oscillating arm, which originates in the inertia of the oscillating flywheel and is transmitted to the oscillating arm by the associated rolling body.
  • the raceway formed on the oscillating flywheel, the raceway formed on the oscillating arm and the rolling body are such that in the reference position, a radial axis passes through the axis of revolution. by a point of contact between the rolling body and the race formed on the oscillating flywheel, and by a point of contact between the rolling body and the raceway formed on the oscillating arm, this radial axis being, in a plane perpendicular to the axis of revolution, perpendicular to the raceway formed on the oscillating flywheel, and perpendicular to the raceway formed on the oscillating arm.
  • the oscillating flywheel has the general shape of a peripheral ring.
  • the oscillating flywheel has a substantially circular radially outer edge.
  • the raceway formed on the oscillating arm is rotated radially outwardly, and is preferably concave in a median section plane perpendicular to the axis of revolution.
  • the raceway formed on the oscillating flywheel is located substantially opposite the raceway formed on the oscillating arm.
  • the raceway formed on the oscillating flywheel is rotated radially inwards and preferably concave, in a median cutting plane perpendicular to the axis of revolution.
  • the raceway of the oscillating flywheel is formed on the central opening of the peripheral ring.
  • there is at least one plane perpendicular to the axis of revolution which intersects the raceway formed in the oscillating arm and the raceway formed in the oscillating flywheel. These raceways are contained in the same plane perpendicular to the axis of revolution.
  • the raceway formed on the oscillating flywheel, the raceway formed on the oscillating arm and the rolling body are such that in the reference position, the rolling body is in a position of removal. maximum relative to the axis of revolution.
  • the raceway formed on the oscillating flywheel, the raceway formed on the oscillating arm and the rolling body are such that in the reference position, a radial axis passing by the axis of revolution and by a point of contact between the rolling body and the raceway formed on the oscillating flywheel is, in a median plane perpendicular to the axis of revolution, perpendicular to the raceway formed on the oscillating flywheel.
  • a radial axis passing through the axis of revolution and a point of contact between the rolling body and the raceway formed on the oscillating arm is, in a median plane perpendicular to the axis of revolution, perpendicular to the raceway formed on the swingarm.
  • the oscillating arm pivots relative to the member to be damped around a pivot axis, preferably fixed relative to the member to be damped, the rolling body having an axis of rotation parallel to the pivot axis.
  • the oscillating arm preferably extends in a circumferential direction, so that its movement is essentially radial with respect to the axis of revolution.
  • the rolling body is a roller, which ensures a relatively large contact area between the rolling body and the raceways.
  • a rolling body consisting of a ball.
  • the raceways will preferably form grooves having, in section through a plane passing through the axis of revolution, a shape in an arc or ogive, for guiding the ball.
  • Such an arrangement may make it possible, if necessary, to take better care of very slight axial or angular fluctuations between the member to be damped and the oscillating flywheel.
  • the mechanism comprises means for securing the oscillating flywheel to the member to be damped when the speed of rotation of the mechanism exceeds a predetermined speed threshold, which in practice is preferably greater than the speed of rotation.
  • a predetermined speed threshold which in practice is preferably greater than the speed of rotation. engine idling, for example a speed threshold greater than 1500 rpm but less than 2500 rpm.
  • the oscillating arm comprises a bearing surface having an abutment function and bearing against the oscillating flywheel under the effect of an elastic deformation of the oscillating arm when the speed rotation of the member to be damped, or that of the oscillating flywheel, exceeds a given threshold.
  • a transmission kinematic chain comprising a filter mechanism as described above, interposed between a crankshaft of an internal combustion engine rotating about the axis. of revolution and a gearbox, the transmission mechanism further comprising an input member kinematically interposed between the crankshaft and the member to be damped, the member to be damped constituting a secondary member rotating about the axis of revolution by report to the input organ.
  • the filtration mechanism according to the invention may constitute a long-stroke damper disposed downstream of a hydro-kinetic converter and a locking clutch of a torque converter, in which case the member to be damped may be a phasing member.
  • the oscillating flywheel is guided in rotation about the axis of revolution relative to the phasing member.
  • the filtration mechanism may constitute a double damping flywheel disposed downstream or upstream of a dry clutch, in which case the member to be damped is preferably the secondary member of this double steering wheel. damper.
  • the transmission kinematic chain comprises elastic return elements for biasing the secondary member towards a reference angular position with respect to the input member.
  • a first filter stage is formed between the input member and the secondary member.
  • the second filtration stage constituted by the oscillating flywheel connected to the secondary member has a filtering characteristic which varies as a function of the speed of rotation. The fluctuations seen by the secondary member being attenuated by the first filtration stage, it is possible to obtain the additional filtering effect sought with oscillating arms and a wheel of reduced masses.
  • the elastic elements at least partially in a volume between the input member and the secondary member, spring housing windows constituting the elastic return elements. It may also be provided if necessary friction elements to dissipate energy during relative angular movements between the input member and the secondary member.
  • one of the primary and secondary members comprises a web and the other of the primary and secondary members comprises two guide rings fixed to one another and located axially on the one hand and on the other. other of the veil.
  • the member to be damped can thus be constituted by the web or one of the washers or be integral with the web or one of the washers.
  • the invention also relates, according to another of its aspects, a torque fluctuation filtration mechanism, comprising a damping member rotating about an axis of revolution, an oscillating flywheel revolving around the axis of revolution relative to the member to be damped, and at least one connecting module allowing an angular displacement of the flywheel oscillating relative to the member to be damped on both sides of a position of reference, the link module comprising at least one oscillating arm pivoting radially relative to the member to be damped, the connection module further comprising a rolling body of rolling connection on a raceway formed on the oscillating arm and on a raceway formed on the oscillating flywheel, characterized in that there is at least one plane perpendicular to the axis of revolution which cuts the oscillating arm , the connecting rolling body and the oscillating flywheel, the connecting rolling body being radially interposed between the raceways formed on the oscillating arm and the flywheel oscillating in said plane.
  • FIG. 1 a schematic view of a torque converter incorporating a mechanism for filtering torque fluctuations according to one embodiment of the invention
  • FIG. 2 is an exploded isometric view of one of the filtration mechanism according to one embodiment of the invention
  • - Figure 3 a partially in front and partially in cross section of the filter mechanism of Figure 2
  • FIG. 4 an axial sectional view of the filtration mechanism of FIG. 2, in the section plane IV of FIG. 3
  • FIG. 5 an axial sectional view of the filtration mechanism of FIG. 2, in the plane of FIG.
  • Figure 6 is an exploded isometric view of an oscillating mechanism of the filtration mechanism of Figure 2;
  • Figure 7 is an isometric view of an oscillating arm of the oscillating mechanism of Figure 6;
  • - Figure 8 a front view of a detail of the oscillating mechanism of Figure 6 in a first end position;
  • Figure 9 is a front view of a detail of the oscillating mechanism of Figure 6 in an intermediate position of maximum radial displacement;
  • Figure 10 is a front view of a detail of the oscillating mechanism of Figure 6 in a second end position;
  • Figure 11 is a front view of a detail of an oscillating mechanism according to an alternative embodiment, in an intermediate position of maximum radial displacement;
  • Figure 12 is a schematic view of a double flywheel incorporating a filter mechanism according to another embodiment of the invention;
  • Figure 13 is a schematic view of a double flywheel incorporating a filter mechanism according to another embodiment of the invention.
  • FIG. 1 is schematically illustrated a torque converter 1 located between a crankshaft 2 and a gearbox input shaft 3.
  • This torque converter comprises in known manner a hydrokinetic converter 4 and a locking clutch 5 arranged in parallel between the crankshaft 2 and an input member 12 of a torque fluctuation filtration mechanism 10 whose output member 14 is integral with the input shaft of the box transmission 3.
  • An intermediate phasing member 15 is interposed between the input member 12 and the output member 14, connected to the input member 12 by a first elastic member 16 of rigidity K1 and to the member output 14 by a second elastic member 17 of rigidity K2.
  • This intermediate member is furthermore connected to an oscillating flywheel 22 by means of connecting modules 26 forming an oscillating mechanism 30.
  • the input and output members 14 are members rotating about a same rotational geometric axis 100, rotatable one by one. relative to the other, and each relative to the intermediate phasing member 15, itself also rotatable about the axis of rotation 100.
  • the oscillating flywheel 22 is likely to oscillate angularly relative to to the intermediate phasing member 15.
  • the first elastic member 16 and the second elastic member 17 are arranged in series between the input member 12 and the output member 14, in the sense that a quasistatic angular displacement in one direction of the output member 14 relative to the input member 12 causes an increase in the elastic potential energy of the two elastic members 16, 17, while a relative angular displacement in the opposite direction causes a decrease in e the elastic potential energy of the two elastic members 16, 17.
  • the input member 12 of the filtration mechanism 10 is constituted by a subassembly comprising a pair of guide rings 12.1, 12.2 fixed to each other in a known manner, a bell (not shown) of the locking clutch 18 attached to the guide ring 12.1 and a turbine hub (not shown) of the hydrokinetic converter 4 attached to the other guide ring 12.2.
  • the two guide washers 12.1, 12.2 delimit between them a volume 200 in which is disposed an outlet web 14.1 fixed to a central hub 14.2 and constituting with the latter the output member 14.
  • the central hub 14.2 is intended to come on the input shaft (not shown) of the gearbox 3.
  • the output sail 14.1 forms a star which, in this embodiment, has three branches 14.3.
  • the guide ring 12.1 is perforated by three large windows 12.11 in a circular arc separated in pairs by three bridges of radial material 12.12.
  • the angular positions of the material bridges 12.12 of the washer 12.1 and the branches 14.3 of the output web 14.1 coincide, but their relative angular positioning can naturally vary with the angular variations between the input member 12 and the output member 14.
  • the intermediate phasing member 15 comprises a phasing web 15.1 provided with three arms 15.2 extending radially inside the volume 44, alternation with the branches 14.3 of the star exit web 14.1.
  • the phasing web 15.1 is rotatably mounted about the central hub 14.2.
  • the two guide rings 12.1, 12.2 are housed springs 16.1, 17.1 to the number of six, three constituting the first elastic member 16 and three constituting the second elastic member 17.
  • the three springs 16.1 constituting the first elastic member 16 are each bandaged between one of the arms 15.2 of the intermediate phasing member 15 and one of the bridges 12.12 formed in the guide ring 12.1, so as to work during relative angular movements between the intermediate phasing member 15 and the input member 12.
  • the three springs 17.1 constituting the second elastic member 17 are each bandaged between an arm 15.2 of the intermediate phasing member 15 and one of the branches 14.3 of the output sail 14.1, so as to work when relative angular movements between the intermediate phasing member 15 and the output member 14.
  • the bulk of the springs 16.1 of the first elas member 16 is greater than that of the springs 17.1 constituting the second elastic member 17, the stiffness K1 of the first elastic member 16 is preferably lower than that K2 of the second elastic member 17, in a ratio K2 / K1 for example between 2 and 5, and preferably between 2 and 3.
  • the intermediate phasing member 15 also comprises a flat annular support piece 15.3, located outside the guide rings 12.1, 12.2.
  • the phasing web 15.1 comprises spacers 15.4 which protrude axially through windows made in the guide ring 12.2 and are inserted in openings 15.5 provided for this purpose in the annular support piece 15.3, so as to secure the annular support piece 15.3 to the phasing web 15.1.
  • the oscillating flywheel 22 constituted by a peripheral ring, is guided in rotation about the axis of revolution 100 relative to the phasing member 15 by means of three pins 15.31 fixed on the annular support piece. 15.3 and sliding on three tracks 22.1 arranged on the oscillating flywheel 22, these tracks also defining end stops 22.2, 22.3 limiting the angular displacement of the oscillating flywheel 22 with respect to the phasing member 15 .
  • the oscillating flywheel 22 is connected to the phasing member 15 by means of three connecting modules 26 arranged at 120 ° from each other around the axis of revolution 100. Each link module 26, shown more precisely in FIGS.
  • the raceway 26.5 is located between the pivot 26.2 and a mass extension 26.7 of the swingarm. A portion of the swingarm also forms a bearing face 26.8.
  • the oscillating arm has a heel 26.9 projecting towards the secondary flywheel 22 and sliding on a curved track 26.10, here convex, which is opposes pivoting of the oscillating arm in the clockwise direction and thus prevents the roller from escaping from the housing formed radially between the raceways 26.5 and 26.6 and axially between the annular support piece 15.3 and a wall 26.11 of the oscillating arm 26.1.
  • the device operates in the following manner. At rest, at zero rotation speed, no centrifugal force is exerted on the oscillating arms 26.1.
  • the oscillating flywheel 22 can be positioned in a reference angular position with respect to the annular support piece 15.3 of the phasing member 15, as shown in FIG. 9.
  • the roller 26.4 of each connection module 26 is is then in a median position with respect to the tracks 26.5,
  • the roll is in the equilibrium position described above, and the resulting forces at the tracks 26.5 and 26.6, themselves radial, generate no return torque.
  • the fluctuations of the relative angular positioning of the phasing member 15 and the oscillating flywheel 22 have the effect of changing the angle of the resultant of the forces transmitted by the oscillating arm 26.1 to the phasing member 15, generating a return torque towards the equilibrium position, which increases with the amplitude of the angular deflection and the square of the rotation speed around the axis of revolution.
  • the oscillating mechanism 30, constituted by the oscillating flywheel 22 connected to the phasing member 15 by the connecting modules 26, behaves like a variable stiffness filter as a function of the speed, which opposes the torque variations of the damping member constituted by the phasing member 15.
  • the oscillating mechanism 30 is intended to damp the phasing member 15 in a critical range where there is evidence of resonance phenomena. As soon as the engine speed is sufficiently high and the natural frequency of the oscillating mechanism 30 is exceeded, the oscillating flywheel 22 oscillates in phase opposition with respect to the phasing member 15.
  • the phasing member 15 is thus biased couples that compensate at least partially, namely on the one hand the input and output torque transmitted by the springs 16 and 17, and secondly an oscillating torque originating in the steering wheel inertia, and transmitted to the phasing member 15 by the rollers 26.4, the oscillating arms 26.1 and the pivots 26.2.
  • the moment of inertia of the oscillating flywheel 22 is thus chosen so that the oscillating mechanism 30 has a very low natural frequency with respect to the frequencies of the torque oscillations at the target engine speed.
  • a radial abutment 26.12 which is a support for the swing arm 26.1 in the intermediate position of maximum displacement.
  • the pivot 26.2 of the oscillating arm is thus secured by securing the oscillating flywheel 22 to the phasing member 15 when the speed of rotation increases.
  • the inertia of the oscillating flywheel 22 then adds to that of the phasing member 15 When the rotational speed continues to increase, the forces being distributed between the stop 26.12, the pivot 26.2, the roller 26.4 and the travel paths. bearing 26.5, 26.6.
  • the oscillating mechanism 30 may also be used in other applications requiring filtration of a rotating member.
  • FIG. 12 is shown a transmission system 1 of a motor vehicle with a dry clutch 5 located between a crankshaft 2 and a gearbox input shaft 3. Downstream of the clutch in the driveline transmission is arranged a filtration mechanism 10 constituting a double damping flywheel and having an input member 12 constituted by a primary flywheel connected to the secondary clutch and an output member 114 constituted by a secondary flywheel secured to the shaft input of the gearbox 3. An elastic member 16 is interposed between the input member and the output member so as to work during angular positioning fluctuations between the primary flywheel 12 and the secondary flywheel 114.
  • An oscillating mechanism 30 according to the invention comprising an oscillating flywheel 22 connected to the secondary flywheel 114 by connecting modules 26, allows attenuation of the vibrati low-revolutions of the secondary steering wheel 114.
  • connection modules can be envisaged: axially between the oscillating flywheel 22 and the input member 12; between the secondary member 14 and the input member 12, or within a housing of the input member 12. It can also provide in the input member 12 a housing for the steering wheel oscillating inertia 22.

Abstract

A mechanism for filtering torque fluctuations comprises a member (15, 114) that is to be damped, rotating about an axis of revolution (100), an oscillating flywheel (22) rotating about the axis of revolution (100) with respect to the member (15, 114) that is to be damped, and at least one connecting module allowing the oscillating flywheel (22) an angular travel with respect to the member (15, 114) that is to be damped on each side of a reference position. The connecting module (26) comprises at least one oscillating arm (26.1) pivoting radially with respect to the member that is to be damped, and a rolling connecting body (26.4) rolling along a raceway (26.5) formed on the oscillating arm (26.1) and along a raceway (26.6) formed on the oscillating flywheel (22).

Description

MECANISME DE FILTRATION DE FLUCTUATIONS DE COUPLE DOMAINE TECHNIQUE DE L'INVENTION  MECHANISM FOR FILTRATION OF TORQUE FLUCTUATIONS TECHNICAL FIELD OF THE INVENTION
[0001] L'invention se rapporte à un mécanisme de filtration des acyclismes d'un moteur à combustion interne, situé en amont d'une boîte de transmission, notamment pour une application à un véhicule automobile, et notamment à un mécanisme de filtration intégré à un convertisseur de couple ou à un mécanisme d'embrayage sec.  The invention relates to a mechanism for filtering the acyclisms of an internal combustion engine, located upstream of a gearbox, in particular for an application to a motor vehicle, including an integrated filtration mechanism to a torque converter or dry clutch mechanism.
ETAT DE LA TECHNIQUE ANTERIEURE STATE OF THE PRIOR ART
[0002] Afin d'atténuer les irrégularités de rotation d'un vilebrequin de moteur à combustion interne, principalement à des vitesses entre la vitesse de ralenti et une vitesse de régime intermédiaire, par exemple environ 2500 tours/min, il a été proposé, dans le document FR2857073 d'accoupler directement au vilebrequin d'un moteur à combustion interne un volant d'inertie atténuateur de vibrations de torsion ou de fluctuations de vitesse de rotation, constitué de deux masses d'inerties coaxiales dont une première est solidaire en rotation du vilebrequin, et comporte une couronne de démarreur et un plateau de réaction d'un embrayage à friction, alors que la deuxième est mobile en rotation par rapport à la première, grâce à des modules de liaison articulés comportant chacun au moins un bras oscillant pivotant par rapport à la première masse d'inertie autour d'un axe parallèle à l'axe de révolution, une masse oscillante positionnée à une extrémité libre du bras oscillant de manière à être mobile dans une direction essentiellement radiale, et une bielle reliant un point intermédiaire du bras oscillant à la deuxième masse d'inertie. Par effet centrifuge, les modules articulés s'opposent à la rotation relative des masses d'inertie en exerçant un couple de rappel sensiblement proportionnel à la rotation relative des deux masses d'inertie et au carré de la vitesse de rotation de la masse d'inertie liée au vilebrequin. Ce dispositif s'avère toutefois particulièrement sensible aux phénomènes d'hystérésis engendrés par notamment par les pivots des modules de liaison articulés. EXPOSE DE L'INVENTION [0003] L'invention vise à remédier aux inconvénients de l'état de la technique et à améliorer la filtration des variations de couple moteur à bas régime, et notamment, à titre indicatif, en dessous de 2000 tours par minutes. In order to reduce the irregularities of rotation of an internal combustion engine crankshaft, mainly at speeds between the idling speed and an intermediate speed, for example about 2500 rpm, it has been proposed, in the document FR2857073 to directly couple to the crankshaft of an internal combustion engine a flywheel attenuating torsional vibrations or rotational speed fluctuations, consisting of two masses of coaxial inertia of which a first is rotationally fixed; of the crankshaft, and comprises a starter ring and a reaction plate of a friction clutch, while the second is rotatable relative to the first, by means of articulated connection modules each comprising at least one pivoting pivoting arm relative to the first mass of inertia around an axis parallel to the axis of revolution, an oscillating mass positioned at a free end of the rotor oscillating so as to be movable in a substantially radial direction, and a connecting rod connecting an intermediate point of the oscillating arm to the second mass of inertia. By centrifugal effect, the articulated modules oppose the relative rotation of the masses of inertia by exerting a return torque substantially proportional to the relative rotation of the two masses of inertia and to the square of the rotational speed of the mass of inertia. inertia linked to the crankshaft. However, this device is particularly sensitive to hysteresis phenomena generated in particular by the pivots of the articulated connection modules. SUMMARY OF THE INVENTION The invention aims to overcome the disadvantages of the state of the art and to improve the filtration of engine torque variations at low speed, and in particular, as an indication, below 2000 revolutions per minute.
[0004] Pour ce faire est proposé, selon un premier aspect de l'invention, un mécanisme de filtration de fluctuation de couple, pouvant notamment être destiné à être interposé entre un vilebrequin d'un moteur à combustion interne tournant autour d'un axe de révolution et une boîte de transmission, et comportant un organe à amortir tournant autour de l'axe de révolution, un volant d'inertie oscillant tournant autour de l'axe de révolution par rapport à l'organe à amortir, et au moins un module de liaison permettant un débattement angulaire du volant d'inertie oscillant par rapport à l'organe à amortir de part et d'autre d'une position de référence, le module de liaison comportant au moins un bras oscillant pivotant radialement par rapport à l'organe à amortir et un corps roulant de liaison roulant sur un chemin de roulement formé sur le bras oscillant et sur un chemin de roulement formé sur le volant d'inertie oscillant. L'organe à amortir est ainsi sollicité par des couples antagonistes qui se compensent au moins partiellement, à savoir d'une part un couple acyclique d'entrée, par exemple en provenance d'un moteur à combustion interne, et d'autre part un couple oscillant entrant par l'articulation de chaque bras oscillant, qui trouve son origine dans l'inertie du volant d'inertie oscillant et est transmis au bras oscillants par le corps roulant associé. To do this is proposed, according to a first aspect of the invention, a torque fluctuation filtration mechanism, which may be intended to be interposed between a crankshaft of an internal combustion engine rotating about an axis of revolution and a gearbox, and having a damping member rotating about the axis of revolution, an oscillating flywheel rotating about the axis of revolution relative to the member to be damped, and at least one connecting module allowing an angular displacement of the flywheel oscillating relative to the member to be damped on either side of a reference position, the connecting module comprising at least one oscillating arm pivoting radially relative to the member for damping and a rolling body rolling connection on a raceway formed on the swing arm and on a raceway formed on the oscillating flywheel. The member to be damped is thus biased by counter-couples which compensate themselves at least partially, namely on the one hand an acyclic input torque, for example coming from an internal combustion engine, and on the other hand an oscillating torque entering through the articulation of each oscillating arm, which originates in the inertia of the oscillating flywheel and is transmitted to the oscillating arm by the associated rolling body.
[0005] Avantageusement, le chemin de roulement formé sur le volant d'inertie oscillant, le chemin de roulement formé sur le bras oscillant et le corps roulant sont tels que dans la position de référence, un axe radial passe par l'axe de révolution, par un point de contact entre le corps roulant et le chemin de roulement formé sur le volant d'inertie oscillant, et par un point de contact entre le corps roulant et le chemin de roulement formé sur le bras oscillant, cet axe radial étant, dans un plan perpendiculaire à l'axe de révolution, perpendiculaire au chemin de roulement formé sur le volant d'inertie oscillant, et perpendiculaire au chemin de roulement formé sur le bras oscillant. [0006] En remplaçant la bielle de l'état de la technique par une liaison de roulement avec un corps roulant, on diminue de manière très significative le coefficient de frottement. Par ailleurs, la liaison ainsi définie est plus compacte qu'une liaison à bielle. Advantageously, the raceway formed on the oscillating flywheel, the raceway formed on the oscillating arm and the rolling body are such that in the reference position, a radial axis passes through the axis of revolution. by a point of contact between the rolling body and the race formed on the oscillating flywheel, and by a point of contact between the rolling body and the raceway formed on the oscillating arm, this radial axis being, in a plane perpendicular to the axis of revolution, perpendicular to the raceway formed on the oscillating flywheel, and perpendicular to the raceway formed on the oscillating arm. By replacing the rod of the state of the art by a rolling connection with a rolling body, it significantly decreases the coefficient of friction. Moreover, the link thus defined is more compact than a connecting rod.
[0007] De préférence, le volant d'inertie oscillant présente la forme générale d'un anneau périphérique. Notamment, le volant d'inertie oscillant a un bord radialement extérieur sensiblement circulaire. [0007] Preferably, the oscillating flywheel has the general shape of a peripheral ring. In particular, the oscillating flywheel has a substantially circular radially outer edge.
[0008] Suivant un mode de réalisation, le chemin de roulement formé sur le bras oscillant est tourné radialement vers l'extérieur, et est de préférence concave dans un plan de coupe médian perpendiculaire à l'axe de révolution. According to one embodiment, the raceway formed on the oscillating arm is rotated radially outwardly, and is preferably concave in a median section plane perpendicular to the axis of revolution.
[0009] Le chemin de roulement formé sur le volant d'inertie oscillant est situé sensiblement en regard du chemin de roulement formé sur le bras oscillant. Suivant un mode de réalisation, le chemin de roulement formé sur le volant d'inertie oscillant est tourné radialement vers l'intérieur et de préférence concave, dans un plan de coupe médian perpendiculaire à l'axe de révolution. Le chemin de roulement du volant d'inertie oscillant est formé sur l'ouverture centrale de l'anneau périphérique. [0010] Avantageusement, il existe au moins un plan perpendiculaire à l'axe de révolution qui coupe le chemin de roulement formé dans le bras oscillant et le chemin de roulement formé dans le volant d'inertie oscillant. Ces chemins de roulement sont contenus dans un même plan perpendiculaire à l'axe de révolution. The raceway formed on the oscillating flywheel is located substantially opposite the raceway formed on the oscillating arm. According to one embodiment, the raceway formed on the oscillating flywheel is rotated radially inwards and preferably concave, in a median cutting plane perpendicular to the axis of revolution. The raceway of the oscillating flywheel is formed on the central opening of the peripheral ring. Advantageously, there is at least one plane perpendicular to the axis of revolution which intersects the raceway formed in the oscillating arm and the raceway formed in the oscillating flywheel. These raceways are contained in the same plane perpendicular to the axis of revolution.
[0011] Préférentiellement, le chemin de roulement formé sur le volant d'inertie oscillant, le chemin de roulement formé sur le bras oscillant et le corps roulant sont tels que dans la position de référence, le corps roulant est dans une position d'éloignement maximal par rapport à l'axe de révolution. Preferably, the raceway formed on the oscillating flywheel, the raceway formed on the oscillating arm and the rolling body are such that in the reference position, the rolling body is in a position of removal. maximum relative to the axis of revolution.
[0012] Suivant un mode de réalisation particulièrement avantageux, le chemin de roulement formé sur le volant d'inertie oscillant, le chemin de roulement formé sur le bras oscillant et le corps roulant sont tels que dans la position de référence, un axe radial passant par l'axe de révolution et par un point de contact entre le corps roulant et le chemin de roulement formé sur le volant d'inertie oscillant est, dans un plan médian perpendiculaire à l'axe de révolution, perpendiculaire au chemin de roulement formé sur le volant d'inertie oscillant. Dans les mêmes conditions, on prévoit de préférence qu'un axe radial passant par l'axe de révolution et par un point de contact entre le corps roulant et le chemin de roulement formé sur le bras oscillant est, dans un plan médian perpendiculaire à l'axe de révolution, perpendiculaire au chemin de roulement formé sur le bras oscillant. On fait ainsi en sorte que dans la position de référence, aucun couple ne soit transmis par le corps roulant ni au bras oscillant, ni au volant d'inertie oscillant. La position relative correspondante de l'organe à amortir et du volant d'inertie oscillant constitue une position de référence qui est atteinte en régime stationnaire en l'absence de fluctuation du couple moteur. Tout mouvement angulaire relatif entre l'organe à amortir et le volant d'inertie oscillant à partir de cette position de référence a pour effet de rapprocher le bras oscillant de l'axe de révolution. According to a particularly advantageous embodiment, the raceway formed on the oscillating flywheel, the raceway formed on the oscillating arm and the rolling body are such that in the reference position, a radial axis passing by the axis of revolution and by a point of contact between the rolling body and the raceway formed on the oscillating flywheel is, in a median plane perpendicular to the axis of revolution, perpendicular to the raceway formed on the oscillating flywheel. In the same conditions, preferably provides that a radial axis passing through the axis of revolution and a point of contact between the rolling body and the raceway formed on the oscillating arm is, in a median plane perpendicular to the axis of revolution, perpendicular to the raceway formed on the swingarm. This ensures that in the reference position, no torque is transmitted by the rolling body neither to the oscillating arm, nor to the oscillating flywheel. The corresponding relative position of the damping member and the oscillating flywheel constitutes a reference position which is reached in stationary mode in the absence of fluctuation of the engine torque. Any relative angular movement between the member to be damped and the flywheel oscillating from this reference position has the effect of bringing the oscillating arm of the axis of revolution.
[0013] De préférence, le bras oscillant pivote par rapport à l'organe à amortir autour d'un axe de pivotement, de préférence fixe par rapport à l'organe à amortir, le corps roulant ayant un axe de rotation parallèle à l'axe de pivotement. Le bras oscillant s'étend de préférence dans une direction circonférentielle, de manière à ce que son mouvement soit essentiellement radial par rapport à l'axe de révolution. Preferably, the oscillating arm pivots relative to the member to be damped around a pivot axis, preferably fixed relative to the member to be damped, the rolling body having an axis of rotation parallel to the pivot axis. The oscillating arm preferably extends in a circumferential direction, so that its movement is essentially radial with respect to the axis of revolution.
[0014] Suivant un mode de réalisation préféré, le corps roulant est un rouleau, ce qui permet d'assurer une zone de contact relativement importante entre le corps roulant et les chemins de roulement. Toutefois, on peut également prévoir un corps roulant constitué d'une bille. Dans ce dernier cas, les chemins de roulement formeront de préférence des gorges présentant, en section par un plan passant par l'axe de révolution, une forme en arc de cercle ou en ogive, pour le guidage de la bille. Une telle disposition peut permettre le cas échéant de mieux prendre en charge de très légères fluctuations axiales ou angulaires entre l'organe à amortir et le volant d'inertie oscillant. According to a preferred embodiment, the rolling body is a roller, which ensures a relatively large contact area between the rolling body and the raceways. However, it is also possible to provide a rolling body consisting of a ball. In the latter case, the raceways will preferably form grooves having, in section through a plane passing through the axis of revolution, a shape in an arc or ogive, for guiding the ball. Such an arrangement may make it possible, if necessary, to take better care of very slight axial or angular fluctuations between the member to be damped and the oscillating flywheel.
[0015] Avantageusement, il existe au moins un plan perpendiculaire à l'axe de révolution qui coupe le bras oscillant, le corps roulant de liaison et le volant d'inertie oscillant. Le corps roulant de liaison est radialement interposé entre les chemins de roulement formés sur le bras oscillant et sur le volant d'inertie oscillant dans le dit plan. [0016] De préférence, le mécanisme comporte des moyens de solidarisation du volant d'inertie oscillant à l'organe à amortir lorsque la vitesse de rotation du mécanisme dépasse un seuil de vitesse prédéterminé, qui en pratique est de préférence supérieur à la vitesse de ralenti du moteur, par exemple un seuil de vitesse supérieur à 1500 tr/min mais inférieur à 2500 tr/min. Advantageously, there is at least one plane perpendicular to the axis of revolution which intersects the oscillating arm, the rolling body connecting and the flywheel oscillating. The rolling body connecting is radially interposed between the raceways formed on the oscillating arm and the flywheel oscillating in said plane. Preferably, the mechanism comprises means for securing the oscillating flywheel to the member to be damped when the speed of rotation of the mechanism exceeds a predetermined speed threshold, which in practice is preferably greater than the speed of rotation. engine idling, for example a speed threshold greater than 1500 rpm but less than 2500 rpm.
[0017] Suivant un mode de réalisation particulièrement avantageux, le bras oscillant comporte une face d'appui ayant fonction de butée et venant en appui contre le volant d'inertie oscillant sous l'effet d'une déformation élastique du bras oscillant lorsque la vitesse de rotation de l'organe à amortir, ou celle du volant d'inertie oscillant, dépasse un seuil donné. According to a particularly advantageous embodiment, the oscillating arm comprises a bearing surface having an abutment function and bearing against the oscillating flywheel under the effect of an elastic deformation of the oscillating arm when the speed rotation of the member to be damped, or that of the oscillating flywheel, exceeds a given threshold.
[0018] Naturellement, il est possible de combiner entre elles les caractéristiques des divers modes de réalisation. Naturally, it is possible to combine the characteristics of the various embodiments with one another.
[0019] Selon un autre aspect de l'invention, celle-ci a trait à une chaîne cinématique de transmission comportant un mécanisme de filtration tel que décrit précédemment, interposé entre un vilebrequin d'un moteur à combustion interne tournant autour de l'axe de révolution et une boîte de transmission, le mécanisme de transmission comportant en outre un organe d'entrée cinématiquement interposé entre le vilebrequin et l'organe à amortir, l'organe à amortir constituant un organe secondaire tournant autour de l'axe de révolution par rapport à l'organe d'entrée. [0020] Suivant un mode de réalisation, le mécanisme de filtration selon l'invention peut constituer un amortisseur à longue course disposé en aval d'un convertisseur hydro-cinétique et d'un embrayage de verrouillage d'un convertisseur de couple, auquel cas l'organe à amortir peut être un organe de phasage. According to another aspect of the invention, it relates to a transmission kinematic chain comprising a filter mechanism as described above, interposed between a crankshaft of an internal combustion engine rotating about the axis. of revolution and a gearbox, the transmission mechanism further comprising an input member kinematically interposed between the crankshaft and the member to be damped, the member to be damped constituting a secondary member rotating about the axis of revolution by report to the input organ. According to one embodiment, the filtration mechanism according to the invention may constitute a long-stroke damper disposed downstream of a hydro-kinetic converter and a locking clutch of a torque converter, in which case the member to be damped may be a phasing member.
[0021] Avantageusement, le volant d'inertie oscillant est guidé en rotation autour de l'axe de révolution par rapport à l'organe de phasage. Advantageously, the oscillating flywheel is guided in rotation about the axis of revolution relative to the phasing member.
[0022] Suivant un autre mode de réalisation, le mécanisme de filtration peut constituer un double volant amortisseur disposé en aval ou en amont d'un embrayage sec, auquel cas l'organe à amortir est de préférence l'organe secondaire de ce double volant amortisseur. [0023] De préférence, la chaîne cinématique de transmission comporte des éléments de rappel élastique pour rappeler l'organe secondaire vers une position angulaire de référence par rapport à l'organe d'entrée. On constitue ainsi, en amont de l'organe secondaire dans la chaîne cinématique de transmission, un premier étage de filtration entre l'organe d'entrée et l'organe secondaire. Le deuxième étage de filtration constitué par le volant d'inertie oscillant relié à l'organe secondaire a une caractéristique de filtration qui varie en fonction de la vitesse de rotation. Les fluctuations vues par l'organe secondaire étant atténuées par le premier étage de filtration, il est possible d'obtenir l'effet supplémentaire de filtration recherché avec des bras oscillants et un volant de masses réduites. According to another embodiment, the filtration mechanism may constitute a double damping flywheel disposed downstream or upstream of a dry clutch, in which case the member to be damped is preferably the secondary member of this double steering wheel. damper. Preferably, the transmission kinematic chain comprises elastic return elements for biasing the secondary member towards a reference angular position with respect to the input member. Thus, upstream of the secondary member in the transmission kinematic chain, a first filter stage is formed between the input member and the secondary member. The second filtration stage constituted by the oscillating flywheel connected to the secondary member has a filtering characteristic which varies as a function of the speed of rotation. The fluctuations seen by the secondary member being attenuated by the first filtration stage, it is possible to obtain the additional filtering effect sought with oscillating arms and a wheel of reduced masses.
[0024] Suivant un mode de réalisation, on peut notamment prévoir de loger les éléments élastiques au moins partiellement dans un volume situé entre l'organe d'entrée et l'organe secondaire, des fenêtres de logement de ressorts constituant les éléments de rappel élastique. [0025] On peut également prévoir le cas échéant des éléments de friction pour dissiper de l'énergie lors des mouvements angulaires relatifs entre l'organe d'entrée et l'organe secondaire. According to one embodiment, it is possible in particular to accommodate the elastic elements at least partially in a volume between the input member and the secondary member, spring housing windows constituting the elastic return elements. . It may also be provided if necessary friction elements to dissipate energy during relative angular movements between the input member and the secondary member.
[0026] Suivant un mode de réalisation, l'un des organes primaire et secondaire comprend un voile et l'autre des organes primaire et secondaire comprend deux rondelles de guidage fixées l'une à l'autre et situées axialement de part et d'autre du voile. L'organe à amortir peut ainsi être constitué par le voile ou l'une des rondelles ou être solidaire du voile ou de l'une des rondelles. According to one embodiment, one of the primary and secondary members comprises a web and the other of the primary and secondary members comprises two guide rings fixed to one another and located axially on the one hand and on the other. other of the veil. The member to be damped can thus be constituted by the web or one of the washers or be integral with the web or one of the washers.
[0027] L'invention a également pour objet, selon un autre de ses aspects, un mécanisme de filtration de fluctuations de couple, comportant un organe à amortir tournant autour d'un axe de révolution, un volant d'inertie oscillant tournant autour de l'axe de révolution par rapport à l'organe à amortir, et au moins un module de liaison permettant un débattement angulaire du volant d'inertie oscillant par rapport à l'organe à amortir de part et d'autre d'une position de référence, le module de liaison comportant au moins un bras oscillant pivotant radialement par rapport à l'organe à amortir, le module de liaison comportant en outre un corps roulant de liaison roulant sur un chemin de roulement formé sur le bras oscillant et sur un chemin de roulement formé sur le volant d'inertie oscillant, caractérisé en ce qu'il existe au moins un plan perpendiculaire à l'axe de révolution qui coupe le bras oscillant, le corps roulant de liaison et le volant d'inertie oscillant, le corps roulant de liaison étant radialement interposé entre les chemins de roulement formés sur le bras oscillant et sur le volant d'inertie oscillant dans le dit plan. The invention also relates, according to another of its aspects, a torque fluctuation filtration mechanism, comprising a damping member rotating about an axis of revolution, an oscillating flywheel revolving around the axis of revolution relative to the member to be damped, and at least one connecting module allowing an angular displacement of the flywheel oscillating relative to the member to be damped on both sides of a position of reference, the link module comprising at least one oscillating arm pivoting radially relative to the member to be damped, the connection module further comprising a rolling body of rolling connection on a raceway formed on the oscillating arm and on a raceway formed on the oscillating flywheel, characterized in that there is at least one plane perpendicular to the axis of revolution which cuts the oscillating arm , the connecting rolling body and the oscillating flywheel, the connecting rolling body being radially interposed between the raceways formed on the oscillating arm and the flywheel oscillating in said plane.
BREVE DESCRIPTION DES FIGURES BRIEF DESCRIPTION OF THE FIGURES
[0028] D'autres caractéristiques et avantages de l'invention ressortiront à la lecture de la description qui suit, en référence aux figures annexées, qui illustrent : - la figure 1, une vue schématique d'un convertisseur de couple intégrant un mécanisme de filtration de fluctuations de couple selon un mode de réalisation de l'invention; la figure 2, une vue isométrique éclatée d'un du mécanisme de filtration selon un mode de réalisation de l'invention ; - la figure 3, une partiellement de face et partiellement en coupe transversale du mécanisme de filtration de la figure 2; la figure 4, une vue en coupe axiale du mécanisme de filtration de la figure 2, dans le plan de coupe IV de la figure 3 la figure 5, une vue en coupe axiale du mécanisme de filtration de la figure 2, dans le plan de coupe V de la figure 3; la figure 6, une vue isométrique éclatée d'un mécanisme oscillant du mécanisme de filtration de la figure 2; la figure 7, une vue isométrique d'un bras oscillant du mécanisme oscillant de la figure 6; - la figure 8, une vue de face d'un détail du mécanisme oscillant de la figure 6 dans une première position de fin de course; la figure 9, une vue de face d'un détail du mécanisme oscillant de la figure 6 dans une position intermédiaire de débattement radial maximal; la figure 10, une vue de face d'un détail du mécanisme oscillant de la figure 6 dans une deuxième position de fin de course; la figure 11, une vue de face d'un détail d'un mécanisme oscillant selon une variante de réalisation, dans une position intermédiaire de débattement radial maximal; la figure 12, une vue schématique d'un double volant d'inertie intégrant un mécanisme de filtration suivant un autre mode de réalisation de l'invention; la figure 13, une vue schématique d'un double volant d'inertie intégrant un mécanisme de filtration suivant un autre mode de réalisation de l'invention. Other features and advantages of the invention will emerge on reading the description which follows, with reference to the appended figures, which illustrate: FIG. 1, a schematic view of a torque converter incorporating a mechanism for filtering torque fluctuations according to one embodiment of the invention; FIG. 2 is an exploded isometric view of one of the filtration mechanism according to one embodiment of the invention; - Figure 3, a partially in front and partially in cross section of the filter mechanism of Figure 2; FIG. 4, an axial sectional view of the filtration mechanism of FIG. 2, in the section plane IV of FIG. 3; FIG. 5, an axial sectional view of the filtration mechanism of FIG. 2, in the plane of FIG. section V of Figure 3; Figure 6 is an exploded isometric view of an oscillating mechanism of the filtration mechanism of Figure 2; Figure 7 is an isometric view of an oscillating arm of the oscillating mechanism of Figure 6; - Figure 8, a front view of a detail of the oscillating mechanism of Figure 6 in a first end position; Figure 9 is a front view of a detail of the oscillating mechanism of Figure 6 in an intermediate position of maximum radial displacement; Figure 10 is a front view of a detail of the oscillating mechanism of Figure 6 in a second end position; Figure 11 is a front view of a detail of an oscillating mechanism according to an alternative embodiment, in an intermediate position of maximum radial displacement; Figure 12 is a schematic view of a double flywheel incorporating a filter mechanism according to another embodiment of the invention; Figure 13 is a schematic view of a double flywheel incorporating a filter mechanism according to another embodiment of the invention.
[0029] Pour plus de clarté, les éléments identiques ou similaires sont repérés par des signes de référence identiques sur l'ensemble des figures. For clarity, the identical or similar elements are identified by identical reference signs throughout the figures.
DESCRIPTION DÉTAILLÉE DE MODES DE REALISATION DETAILED DESCRIPTION OF EMBODIMENTS
[0030] Sur la figure 1 est illustré de façon schématique un convertisseur de couple 1 situé entre un vilebrequin 2 et un arbre d'entrée de boîte de transmission 3. Ce convertisseur de couple comporte de manière connue en soi un convertisseur hydro-cinétique 4 et un embrayage de verrouillage 5 disposés en parallèle entre le vilebrequin 2 et un organe d'entrée 12 d'un mécanisme de filtration de fluctuation du couple 10 dont l'organe de sortie 14 est solidaire à l'arbre d'entrée de la boîte transmission 3. Un organe intermédiaire de phasage 15 est interposé entre l'organe d'entrée 12 et l'organe de sortie 14, relié à l'organe d'entrée 12 par un premier organe élastique 16 de rigidité Kl et à l'organe de sortie 14 par un deuxième organe élastique 17 de rigidité K2. Cet organe intermédiaire est en outre relié à un volant d'inertie oscillant 22 par l'intermédiaire de modules de liaison 26 formant un mécanisme oscillant 30. [0031] Comme il apparaîtra plus clairement dans les illustrations structurelles des figures 2 à 5, les organes d'entrée 12 et de sortie 14 sont des organes tournant autour d'un même axe géométrique de rotation 100, mobiles en rotation l'un par rapport à l'autre, et chacun par rapport à l'organe intermédiaire de phasage 15, lui- même également mobile en rotation autour de l'axe de rotation 100. Le volant d'inertie oscillant 22 est susceptible d'osciller angulairement par rapport à l'organe intermédiaire de phasage 15. Le premier organe élastique 16 et le deuxième organe élastique 17 sont disposés en série entre l'organe d'entrée 12 et l'organe de sortie 14, au sens où un déplacement angulaire quasistatique dans un sens de l'organe de sortie 14 par rapport à l'organe d'entrée 12 provoque une augmentation de l'énergie potentielle élastique des deux organes élastiques 16, 17, alors qu'un déplacement angulaire relatif dans le sens opposé provoque une diminution de l'énergie potentielle élastique des deux organes élastiques 16, 17. In Figure 1 is schematically illustrated a torque converter 1 located between a crankshaft 2 and a gearbox input shaft 3. This torque converter comprises in known manner a hydrokinetic converter 4 and a locking clutch 5 arranged in parallel between the crankshaft 2 and an input member 12 of a torque fluctuation filtration mechanism 10 whose output member 14 is integral with the input shaft of the box transmission 3. An intermediate phasing member 15 is interposed between the input member 12 and the output member 14, connected to the input member 12 by a first elastic member 16 of rigidity K1 and to the member output 14 by a second elastic member 17 of rigidity K2. This intermediate member is furthermore connected to an oscillating flywheel 22 by means of connecting modules 26 forming an oscillating mechanism 30. As will become more clearly apparent in the structural illustrations of FIGS. 2 to 5, the input and output members 14 are members rotating about a same rotational geometric axis 100, rotatable one by one. relative to the other, and each relative to the intermediate phasing member 15, itself also rotatable about the axis of rotation 100. The oscillating flywheel 22 is likely to oscillate angularly relative to to the intermediate phasing member 15. The first elastic member 16 and the second elastic member 17 are arranged in series between the input member 12 and the output member 14, in the sense that a quasistatic angular displacement in one direction of the output member 14 relative to the input member 12 causes an increase in the elastic potential energy of the two elastic members 16, 17, while a relative angular displacement in the opposite direction causes a decrease in e the elastic potential energy of the two elastic members 16, 17.
[0032] Structurellement, l'organe d'entrée 12 du mécanisme de filtration 10 est constitué par sous-ensemble comportant une paire de rondelles de guidage 12.1, 12.2 fixées l'une à l'autre de façon en soi connue, une cloche (non illustrée) de l'embrayage de verrouillage 18 fixée à la rondelle de guidage 12.1 et un moyeu de turbine (non illustré) du convertisseur hydrocinétique 4 fixé à l'autre rondelle de guidage 12.2. Les deux rondelles de guidage 12.1, 12.2 délimitent entre elles un volume 200 dans lequel est disposé un voile de sortie 14.1 fixé à un moyeu central 14.2 et constituant avec ce dernier l'organe de sortie 14. Le moyeu central 14.2 est destiné à venir s'emmancher sur l'arbre d'entrée (non représenté) de la boîte de transmission 3. Le voile de sortie 14.1 forme une étoile qui, dans ce mode de réalisation, présente trois branches 14.3. La rondelle de guidage 12.1 est ajourée par trois grandes fenêtres 12.11 en arc de cercle séparées deux à deux par trois ponts de matière radiaux 12.12. Sur les figures, les positions angulaires des ponts de matière 12.12 de la rondelle 12.1 et des branches 14.3 du voile de sortie 14.1 coïncident, mais leur positionnement angulaire relatif peut naturellement varier avec les variations angulaires entre organe d'entrée 12 et organe de sortie 14. [0033] L'organe intermédiaire de phasage 15 comporte un voile de phasage 15.1 pourvu de trois bras 15.2 s'étendant radialement à l'intérieur du volume 44, en alternance avec les branches 14.3 du voile de sortie en étoile 14.1. Le voile de phasage 15.1 est monté de manière à pouvoir tourner autour du moyeu central 14.2. Structurally, the input member 12 of the filtration mechanism 10 is constituted by a subassembly comprising a pair of guide rings 12.1, 12.2 fixed to each other in a known manner, a bell ( not shown) of the locking clutch 18 attached to the guide ring 12.1 and a turbine hub (not shown) of the hydrokinetic converter 4 attached to the other guide ring 12.2. The two guide washers 12.1, 12.2 delimit between them a volume 200 in which is disposed an outlet web 14.1 fixed to a central hub 14.2 and constituting with the latter the output member 14. The central hub 14.2 is intended to come on the input shaft (not shown) of the gearbox 3. The output sail 14.1 forms a star which, in this embodiment, has three branches 14.3. The guide ring 12.1 is perforated by three large windows 12.11 in a circular arc separated in pairs by three bridges of radial material 12.12. In the figures, the angular positions of the material bridges 12.12 of the washer 12.1 and the branches 14.3 of the output web 14.1 coincide, but their relative angular positioning can naturally vary with the angular variations between the input member 12 and the output member 14. The intermediate phasing member 15 comprises a phasing web 15.1 provided with three arms 15.2 extending radially inside the volume 44, alternation with the branches 14.3 of the star exit web 14.1. The phasing web 15.1 is rotatably mounted about the central hub 14.2.
[0034] Dans le volume délimité par les deux rondelles de guidage 12.1, 12.2 sont logés des ressorts 16.1, 17.1 au nombre de six, trois constituant le premier organe élastique 16 et trois constituant le deuxième organe élastique 17. Les trois ressorts 16.1 constituant le premier organe élastique 16 sont bandés chacun entre un des bras 15.2 de l'organe intermédiaire de phasage 15 et un des ponts 12.12 constitués dans la rondelle de guidage 12.1, de manière à travailler lors des mouvements angulaires relatifs entre l'organe intermédiaire de phasage 15 et l'organe d'entrée 12. Les trois ressorts 17.1 constituant le deuxième organe élastique 17 sont bandés chacun entre un bras 15.2 de l'organe intermédiaire de phasage 15 et une des branches 14.3 du voile de sortie 14.1, de manière à travailler lors des mouvements angulaires relatifs entre l'organe intermédiaire de phasage 15 et l'organe de sortie 14. On notera que l'encombrement des ressorts 16.1 du premier organe élastique 16 est plus important que celui des ressorts 17.1 constituant le deuxième organe élastique 17, la rigidité Kl du premier organe élastique 16 étant de préférence inférieure à celle K2 du deuxième organe élastique 17, dans un rapport K2/K1 par exemple compris entre 2 et 5, et de préférence entre 2 et 3. In the volume defined by the two guide rings 12.1, 12.2 are housed springs 16.1, 17.1 to the number of six, three constituting the first elastic member 16 and three constituting the second elastic member 17. The three springs 16.1 constituting the first elastic member 16 are each bandaged between one of the arms 15.2 of the intermediate phasing member 15 and one of the bridges 12.12 formed in the guide ring 12.1, so as to work during relative angular movements between the intermediate phasing member 15 and the input member 12. The three springs 17.1 constituting the second elastic member 17 are each bandaged between an arm 15.2 of the intermediate phasing member 15 and one of the branches 14.3 of the output sail 14.1, so as to work when relative angular movements between the intermediate phasing member 15 and the output member 14. It will be noted that the bulk of the springs 16.1 of the first elas member 16 is greater than that of the springs 17.1 constituting the second elastic member 17, the stiffness K1 of the first elastic member 16 is preferably lower than that K2 of the second elastic member 17, in a ratio K2 / K1 for example between 2 and 5, and preferably between 2 and 3.
[0035] L'organe intermédiaire de phasage 15 comporte également une pièce annulaire plate de support 15.3, située à l'extérieur des rondelles de guidage 12.1, 12.2. Le voile de phasage 15.1 comporte des entretoises 15.4 qui font saillie axialement au travers de fenêtres pratiquées dans la rondelle de guidage 12.2 et viennent s'insérer dans des ouvertures 15.5 prévues à cet effet dans la pièce annulaire de support 15.3, de manière à solidariser la pièce annulaire de support 15.3 au voile de phasage 15.1. The intermediate phasing member 15 also comprises a flat annular support piece 15.3, located outside the guide rings 12.1, 12.2. The phasing web 15.1 comprises spacers 15.4 which protrude axially through windows made in the guide ring 12.2 and are inserted in openings 15.5 provided for this purpose in the annular support piece 15.3, so as to secure the annular support piece 15.3 to the phasing web 15.1.
[0036] Le volant d'inertie oscillant 22, constitué par un anneau périphérique, est guidé en rotation autour de l'axe de révolution 100 par rapport à l'organe de phasage 15 grâce à trois pions 15.31 fixés sur la pièce annulaire de support 15.3 et glissant sur trois pistes 22.1 aménagées sur le volant d'inertie oscillant 22, ces pistes définissant également des butées de fin de course 22.2, 22.3 limitant le débattement angulaire du volant d'inertie oscillant 22 par rapport à l'organe de phasage 15. Afin d'amortir les fluctuations de couple de l'organe de phasage, le volant d'inertie oscillant 22 est lié à l'organe de phasage 15 par l'intermédiaire de trois modules de liaison 26 disposés à 120° les uns des autres autour de l'axe de révolution 100. Chaque module de liaison 26, illustré plus précisément sur les figures 6 à 10, comporte un bras oscillant 26.1 articulé à la pièce annulaire de support 15.3 par l'intermédiaire d'un pivot 26.2 pour pivoter autour d'un axe de pivotement 200 parallèle à l'axe de révolution 100, et un corps roulant 26.4, en l'espèce un rouleau, roulant sur un chemin de roulement 26.5 formé sur le bras oscillant 26.1 et sur un chemin de roulement 26.6 formé sur le volant d'inertie oscillant 22. Le chemin de roulement 26.5 formé sur le bras oscillant 26.1 est tourné radialement vers l'extérieur et vers le chemin de roulement 26.6 formé sur le volant d'inertie oscillant 22, qui lui est tourné radialement vers l'intérieur. Les deux chemins de roulementThe oscillating flywheel 22, constituted by a peripheral ring, is guided in rotation about the axis of revolution 100 relative to the phasing member 15 by means of three pins 15.31 fixed on the annular support piece. 15.3 and sliding on three tracks 22.1 arranged on the oscillating flywheel 22, these tracks also defining end stops 22.2, 22.3 limiting the angular displacement of the oscillating flywheel 22 with respect to the phasing member 15 . To to dampen the torque fluctuations of the phasing member, the oscillating flywheel 22 is connected to the phasing member 15 by means of three connecting modules 26 arranged at 120 ° from each other around the axis of revolution 100. Each link module 26, shown more precisely in FIGS. 6 to 10, comprises an oscillating arm 26.1 hinged to the annular support piece 15.3 via a pivot 26.2 to pivot around it. a pivot axis 200 parallel to the axis of revolution 100, and a rolling body 26.4, in this case a roller, rolling on a race 26.5 formed on the swing arm 26.1 and on a race 26.6 formed on the oscillating flywheel 22. The raceway 26.5 formed on the oscillating arm 26.1 is turned radially outwards and towards the raceway 26.6 formed on the oscillating flywheel 22, which is turned radially towards it. inside. The two raceways
26.5, 26.6 sont concaves en coupe transversale perpendiculaire à l'axe de révolution 100. Le chemin de roulement 26.5 est situé entre le pivot 26.2 et un prolongement massique 26.7 du bras oscillant. Une partie du bras oscillant forme également une face d'appui 26.8. À l'opposé du chemin de roulement 26.5 et du prolongement massique 26.7 par rapport au pivot 26.2, le bras oscillant présente un talon 26.9 se projetant vers le volant d'inertie secondaire 22 et glissant sur une piste incurvée 26.10, ici convexe, qui s'oppose au pivotement du bras oscillant dans le sens horaire et évite ainsi que le rouleau s'échappe du logement constitué radialement entre les chemins de roulement 26.5 et 26.6 et axialement entre la pièce annulaire de support 15.3 et une paroi 26.11 du bras oscillant 26.1. 26.5, 26.6 are concave in cross-section perpendicular to the axis of revolution 100. The raceway 26.5 is located between the pivot 26.2 and a mass extension 26.7 of the swingarm. A portion of the swingarm also forms a bearing face 26.8. Opposite the race 26.5 and the mass extension 26.7 relative to the pivot 26.2, the oscillating arm has a heel 26.9 projecting towards the secondary flywheel 22 and sliding on a curved track 26.10, here convex, which is opposes pivoting of the oscillating arm in the clockwise direction and thus prevents the roller from escaping from the housing formed radially between the raceways 26.5 and 26.6 and axially between the annular support piece 15.3 and a wall 26.11 of the oscillating arm 26.1.
[0037] Le dispositif fonctionne de la manière suivante. Au repos, à vitesse de rotation nulle, aucune force centrifuge ne s'exerce sur les bras oscillants 26.1. On peut positionner le volant d'inertie oscillant 22 dans une position angulaire de référence par rapport à la pièce annulaire de support 15.3 de l'organe de phasage 15, comme illustré sur la figure 9. Le rouleau 26.4 de chaque module de liaison 26 se trouve alors dans une position médiane par rapport aux chemins de roulement 26.5,The device operates in the following manner. At rest, at zero rotation speed, no centrifugal force is exerted on the oscillating arms 26.1. The oscillating flywheel 22 can be positioned in a reference angular position with respect to the annular support piece 15.3 of the phasing member 15, as shown in FIG. 9. The roller 26.4 of each connection module 26 is is then in a median position with respect to the tracks 26.5,
26.6, et l'on peut tracer, dans un plan perpendiculaire à l'axe de révolution 100, un axe radial 300 passant par l'axe de révolution, par un point de contact entre le rouleau et le chemin de roulement formé sur le bras oscillant et par un point de contact entre le rouleau 26.4 et le chemin de roulement 26.5 formé sur le volant d'inertie oscillant 22, cet axe 300 étant perpendiculaire aux deux chemins de roulement 26.5, 26.6, au niveau des deux points de contact. Cette position de référence est donc une position d'équilibre. À partir de cette position angulaire d'équilibre, toute rotation relative du volant d'inertie oscillant 22 par rapport à l'organe de phasage 15, dans une direction ou l'autre, contribue a rapprocher le prolongement massique 26.7 des bras oscillants 26.1 de l'axe de révolution. 26.6, and it is possible to draw, in a plane perpendicular to the axis of revolution 100, a radial axis 300 passing through the axis of revolution, by a point of contact between the roller and the race formed on the arm oscillating and by a point of contact between the roller 26.4 and the race 26.5 formed on the steering wheel oscillating inertia 22, this axis 300 being perpendicular to the two raceways 26.5, 26.6, at the two points of contact. This reference position is therefore a position of equilibrium. From this equilibrium angular position, any relative rotation of the oscillating flywheel 22 with respect to the phasing member 15, in one direction or the other, contributes to bringing the mass extension 26.7 of the oscillating arms 26.1 closer to one another. the axis of revolution.
[0038] Lorsque le vilebrequin 2 tourne à faible vitesse, les fluctuations de couple moteur ne sont pas filtrées efficacement par les organes élastiques 16, 17 du mécanisme de filtration 10. À ce régime, les fluctuations de couple à chaque allumage de cylindre sont transmises à l'organe de phasage 15 et font fluctuer le positionnement angulaire relatif de l'organe de phasage 15 et du volant oscillant 22, en retard de phase. Le mécanisme de liaison constitué par les trois modules articulés 26 permet un débattement angulaire du volant d'inertie oscillant 22 par rapport à l'organe de phasage 15 de part et d'autre de la position d'équilibre de la figure 9. Chaque bras oscillant 26.1, en tournant avec l'organe de phasage 15 autour de l'axe de révolution 100, applique, par l'effet centrifuge sur le prolongement massique 26.7, un effort sur le rouleau 26.4 dans la direction définie par les deux chemins de roulement 26.5 et 26.6. Lorsque le système est dans la position d'équilibre, le rouleau est dans la position d'équilibre décrite précédemment, et les efforts résultants au niveau des chemins de roulement 26.5 et 26.6, eux-mêmes radiaux, n'engendrent aucun couple de rappel. Les fluctuations du positionnement angulaire relatif de l'organe de phasage 15 et du volant oscillant 22 ont pour effet de changer l'angle de la résultante des efforts transmis par le bras oscillant 26.1 à l'organe de phasage 15, engendrant un couple de rappel vers la position d'équilibre, qui augmente avec l'amplitude du débattement angulaire et le carré de la vitesse de rotation autour de l'axe de révolution. Le mécanisme oscillant 30, constitué par le volant oscillant 22 relié à l'organe de phasage 15 par les modules de liaison 26, se comporte comme un filtre à raideur variable en fonction de la vitesse, qui s'oppose aux variations de couple de l'organe à amortir constitué par l'organe de phasage 15. [0039] Lorsque la vitesse de rotation autour de l'axe de révolution augmente, la résultante des efforts centrifuges appliqués par le bras oscillant 26.1 sur le rouleau 26.4 augmente et l'amplitude des débattements angulaires entre l'organe de phasage 15 et le volant oscillant 24 diminue. Le bras oscillant tend à se déformer de manière élastique et la face d'appui 26.8 du bras oscillant se rapproche progressivement du volant d'inertie oscillant 22. Au-delà d'une vitesse critique donnée, par exemple 2200 tr/min, le face d'appui 26.8 du bras oscillant 26.1 entre en contact avec le pion 15.31, ce qui a pour effet de limiter l'effort sur le rouleau 26.4 et sur le pivot 26.2. When the crankshaft 2 rotates at low speed, the motor torque fluctuations are not effectively filtered by the elastic members 16, 17 of the filter mechanism 10. At this speed, the torque fluctuations at each cylinder ignition are transmitted. to the phasing member 15 and make fluctuate the relative angular positioning of the phasing member 15 and the oscillating wheel 22, late phase. The linking mechanism constituted by the three articulated modules 26 allows an angular displacement of the oscillating flywheel 22 with respect to the phasing member 15 on either side of the equilibrium position of FIG. 9. Each arm oscillating 26.1, rotating with the phasing member 15 about the axis of revolution 100, applies, by the centrifugal effect on the mass extension 26.7, a force on the roller 26.4 in the direction defined by the two raceways 26.5 and 26.6. When the system is in the equilibrium position, the roll is in the equilibrium position described above, and the resulting forces at the tracks 26.5 and 26.6, themselves radial, generate no return torque. The fluctuations of the relative angular positioning of the phasing member 15 and the oscillating flywheel 22 have the effect of changing the angle of the resultant of the forces transmitted by the oscillating arm 26.1 to the phasing member 15, generating a return torque towards the equilibrium position, which increases with the amplitude of the angular deflection and the square of the rotation speed around the axis of revolution. The oscillating mechanism 30, constituted by the oscillating flywheel 22 connected to the phasing member 15 by the connecting modules 26, behaves like a variable stiffness filter as a function of the speed, which opposes the torque variations of the damping member constituted by the phasing member 15. When the speed of rotation about the axis of revolution increases, the resultant centrifugal forces applied by the oscillating arm 26.1 on the roller 26.4 increases and the amplitude of the angular deflections between the phasing member 15 and the oscillating flywheel 24 decreases. The oscillating arm tends to deform elastically and the bearing surface 26.8 of the oscillating arm progressively approaches the oscillating flywheel 22. Beyond a given critical speed, for example 2200 rpm, the face 26.8 of the swing arm 26.1 comes into contact with the pin 15.31, which has the effect of limiting the force on the roller 26.4 and the pivot 26.2.
[0040] Le mécanisme oscillant 30 est destiné à amortir l'organe de phasage 15 dans une plage critique où l'on constate des phénomènes de résonnance. Dès que le régime moteur est suffisamment élevé et que la fréquence propre du mécanisme oscillant 30 est dépassée, le volant d'inertie oscillant 22 oscille en opposition de phase par rapport à l'organe de phasage 15. L'organe de phasage 15 est ainsi sollicité par des couples antagonistes qui se compensent au moins partiellement, à savoir d'une part les couples d'entrée et de sortie transmis par les ressorts 16 et 17, et d'autre part un couple oscillant trouvant son origine dans le volant d'inertie, et transmis à l'organe de phasage 15 par les rouleaux 26.4, les bras oscillants 26.1 et les pivots 26.2. Le moment d'inertie du volant d'inertie oscillant 22 est donc choisi de manière à ce que le mécanisme oscillant 30 ait une fréquence propre très faible par rapport à aux fréquences des oscillations de couple au régime moteur visé. The oscillating mechanism 30 is intended to damp the phasing member 15 in a critical range where there is evidence of resonance phenomena. As soon as the engine speed is sufficiently high and the natural frequency of the oscillating mechanism 30 is exceeded, the oscillating flywheel 22 oscillates in phase opposition with respect to the phasing member 15. The phasing member 15 is thus biased couples that compensate at least partially, namely on the one hand the input and output torque transmitted by the springs 16 and 17, and secondly an oscillating torque originating in the steering wheel inertia, and transmitted to the phasing member 15 by the rollers 26.4, the oscillating arms 26.1 and the pivots 26.2. The moment of inertia of the oscillating flywheel 22 is thus chosen so that the oscillating mechanism 30 has a very low natural frequency with respect to the frequencies of the torque oscillations at the target engine speed.
[0041] En combinant le mécanisme de filtration de couple 10 avec le mécanisme oscillant 30, on bénéficie de l'excellente atténuation des vibrations de l'organe de phasage 15 aux bas régimes, puis on vient bloquer le mécanisme oscillant 30 à plus haut régime, ce blocage du volant oscillant 22 ayant pour effet une augmentation de l'inertie de l'organe de phasage 15. On évite ainsi une usure prématurée des modules de liaison 26. [0042] Le profil des chemins de roulement 26.5, 26.6 peut être adapté à chaque application pour obtenir une courbe de réponse adaptée. By combining the torque filtration mechanism 10 with the oscillating mechanism 30, we benefit from the excellent attenuation of the vibrations of the phasing member 15 at low speeds, then we come to block the oscillating mechanism 30 at higher speeds. this blocking of the oscillating flywheel 22 having the effect of increasing the inertia of the phasing member 15. This avoids premature wear of the connection modules 26. The profile of the raceways 26.5, 26.6 can be adapted to each application to obtain a suitable response curve.
[0043] Suivant une variante illustrée sur la figure 11, on prévoit sur le volant d'inertie oscillant 22 une butée radiale 26.12 qui constitue un appui pour le bras oscillant 26.1 dans la position intermédiaire de débattement maximal. On ménage ainsi le pivot 26.2 du bras oscillant en solidarisant le volant d'inertie oscillant 22 à l'organe de phasage 15 lorsque la vitesse de rotation augmente. L'inertie du volant oscillant 22 s'ajoute alors à celle de l'organe de phasage 15 Lorsque la vitesse de rotation continue d'augmenter, les efforts étant répartis entre la butée 26.12, le pivot 26.2, le rouleau 26.4 et les chemins de roulement 26.5, 26.6. [0044] Le mécanisme oscillant 30 peut également être utilisé dans d'autres applications nécessitant une filtration d'un organe tournant. On peut notamment utiliser le mécanisme oscillant pour amortir certains régimes vibratoires d'un double volant amortisseur disposé dans une chaîne cinématique de transmission entre un vilebrequin et une boîte de transmission comportant un embrayage sec. C'est ce qui a été illustré de façon schématique et fonctionnelle sur les figures 12 et 13. According to a variant illustrated in Figure 11, there is provided on the oscillating flywheel 22 a radial abutment 26.12 which is a support for the swing arm 26.1 in the intermediate position of maximum displacement. The pivot 26.2 of the oscillating arm is thus secured by securing the oscillating flywheel 22 to the phasing member 15 when the speed of rotation increases. The inertia of the oscillating flywheel 22 then adds to that of the phasing member 15 When the rotational speed continues to increase, the forces being distributed between the stop 26.12, the pivot 26.2, the roller 26.4 and the travel paths. bearing 26.5, 26.6. The oscillating mechanism 30 may also be used in other applications requiring filtration of a rotating member. In particular, it is possible to use the oscillating mechanism to dampen certain vibratory regimes of a double damping flywheel arranged in a transmission kinematic chain between a crankshaft and a gearbox comprising a dry clutch. This is illustrated schematically and functionally in Figures 12 and 13.
[0045] Sur la figure 12 est illustrée une chaîne cinématique de transmission 1 de véhicule automobile comportant un embrayage sec 5 situé entre un vilebrequin 2 et un arbre d'entrée de boîte de transmission 3. En aval de l'embrayage dans la chaîne cinématique de transmission est disposé un mécanisme de filtration 10 constituant un double volant amortisseur et comportant un organe d'entrée 12 constitué par un volant primaire relié au secondaire de l'embrayage et un organe de sortie 114 constitué par un volant secondaire solidaire à l'arbre d'entrée de la boîte transmission 3. Un organe élastique 16 est interposé entre l'organe d'entrée et l'organe de sortie de manière à travailler lors de fluctuations de positionnement angulaire entre volant primaire 12 et volant secondaire 114. Un mécanisme oscillant 30 selon l'invention, comportant un volant d'inertie oscillant 22 relié au volant secondaire 114 par des modules de liaison 26, permet une atténuation des vibrations à bas régime du volant secondaire 114. In Figure 12 is shown a transmission system 1 of a motor vehicle with a dry clutch 5 located between a crankshaft 2 and a gearbox input shaft 3. Downstream of the clutch in the driveline transmission is arranged a filtration mechanism 10 constituting a double damping flywheel and having an input member 12 constituted by a primary flywheel connected to the secondary clutch and an output member 114 constituted by a secondary flywheel secured to the shaft input of the gearbox 3. An elastic member 16 is interposed between the input member and the output member so as to work during angular positioning fluctuations between the primary flywheel 12 and the secondary flywheel 114. An oscillating mechanism 30 according to the invention, comprising an oscillating flywheel 22 connected to the secondary flywheel 114 by connecting modules 26, allows attenuation of the vibrati low-revolutions of the secondary steering wheel 114.
[0046] La configuration illustrée sur la figure 13 diffère de la précédente par l'emplacement du double volant amortisseur 10, cinématiquement interposé entre le vilebrequin 2 et un double embrayage 5 permettant d'entraîner deux arbres d'entrée coaxiaux 3.1, 3.2 d'une boîte de transmission 3. The configuration illustrated in Figure 13 differs from the previous by the location of the double damping flywheel 10, kinematically interposed between the crankshaft 2 and a double clutch 5 for driving two coaxial input shafts 3.1, 3.2 d ' a gearbox 3.
[0047] Dans les deux modes de réalisation des figures 12 et, 13, la structure de modules de liaison et celle du volant d'inertie oscillant sont identiques à ce qui a été décrit sur les figures 1 à 11. [0048] D'autres variantes sont naturellement possibles. Différents emplacements des modules de liaison peuvent être envisagés: axialement entre le volant d'inertie oscillant 22 et l'organe d'entrée 12; entre l'organe secondaire 14 et l'organe d'entrée 12, ou à l'intérieur d'un logement de l'organe d'entrée 12. On peut également prévoir dans l'organe d'entrée 12 un logement pour le volant d'inertie oscillant 22. In both embodiments of Figures 12 and 13, the link module structure and that of the oscillating flywheel are identical to what has been described in Figures 1 to 11. Other variants are naturally possible. Different locations of the connection modules can be envisaged: axially between the oscillating flywheel 22 and the input member 12; between the secondary member 14 and the input member 12, or within a housing of the input member 12. It can also provide in the input member 12 a housing for the steering wheel oscillating inertia 22.

Claims

REVENDICATIONS
Mécanisme de filtration de fluctuations de couple, comportant un organe à amortir (15, 114) tournant autour d'un axe de révolution (100), un volant d'inertie oscillant (22) tournant autour de l'axe de révolution (100) par rapport à l'organe à amortir (15, 114), et au moins un module de liaison permettant un débattement angulaire du volant d'inertie oscillant (22) par rapport à l'organe à amortir (15, 114) de part et d'autre d'une position de référence, le module de liaison (26) comportant au moins un bras oscillant (26.1) pivotant radialement par rapport à l'organe à amortir, le module de liaison comportant en outre un corps roulant de liaison (26.4) roulant sur un chemin de roulement (26.5) formé sur le bras oscillant (26.1) et sur un chemin de roulement (26.6) formé sur le volant d'inertie oscillant (22), Mechanism for filtering torque fluctuations, comprising a damping member (15, 114) rotating around an axis of revolution (100), an oscillating flywheel (22) rotating around the axis of revolution (100) relative to the member to be damped (15, 114), and at least one connecting module allowing an angular displacement of the oscillating flywheel (22) with respect to the member to be damped (15, 114) from another of a reference position, the connecting module (26) comprising at least one oscillating arm (26.1) pivoting radially relative to the member to be damped, the connection module further comprising a connecting rolling body ( 26.4) rolling on a raceway (26.5) formed on the swingarm (26.1) and on a raceway (26.6) formed on the oscillating flywheel (22),
caractérisé en ce que le chemin de roulement (26.6) formé sur le volant d'inertie oscillant (22), le chemin de roulement (26.5) formé sur le bras oscillant (26.1) et le corps roulant (26.4) sont tels que dans la position de référence, un axe radial (300) passe par l'axe de révolution (100), par un point de contact entre le corps roulant (26.4) et le chemin de roulement (26.6) formé sur le volant d'inertie oscillant (22), et par un point de contact entre le corps roulant (26.4) et le chemin de roulement (26.5) formé sur le bras oscillant (26.1), characterized in that the raceway (26.6) formed on the oscillating flywheel (22), the raceway (26.5) formed on the swingarm (26.1) and the rolling body (26.4) are such that in the reference position, a radial axis (300) passes through the axis of revolution (100), by a point of contact between the rolling body (26.4) and the raceway (26.6) formed on the oscillating flywheel ( 22), and by a point of contact between the rolling body (26.4) and the raceway (26.5) formed on the swinging arm (26.1),
cet axe radial (300) étant, dans un plan perpendiculaire à l'axe de révolution (100), perpendiculaire au chemin de roulement (26.6) formé sur le volant d'inertie oscillant (22), et perpendiculaire au chemin de roulement (26.5) formé sur le bras oscillant (26.1). this radial axis (300) being, in a plane perpendicular to the axis of revolution (100), perpendicular to the raceway (26.6) formed on the oscillating flywheel (22), and perpendicular to the raceway (26.5 ) formed on the swingarm (26.1).
Mécanisme de filtration selon la revendication 1, caractérisé en ce que le chemin de roulement (26.5) formé sur le bras oscillant (26.1) et le chemin de roulement (26.6) formé sur le volant d'inertie oscillant (22) sont conformés de façon telle que le couple antagoniste augmente avec la vitesse de rotation et avec l'amplitude du débattement angulaire. Filtration mechanism according to claim 1, characterized in that the raceway (26.5) formed on the oscillating arm (26.1) and the raceway (26.6) formed on the oscillating flywheel (22) are shaped such that the counter-torque increases with the speed of rotation and with the amplitude of the angular deflection.
3. Mécanisme de filtration selon l'une quelconque des revendications précédentes, caractérisé en ce que le chemin de roulement (26.5) formé sur le bras oscillant (26.1) est tourné radialement vers l'extérieur. 3. Filtration mechanism according to any one of the preceding claims, characterized in that the raceway (26.5) formed on the oscillating arm (26.1) is rotated radially outwardly.
4. Mécanisme de filtration selon l'une quelconque des revendications précédentes, caractérisé en ce que le chemin de roulement (26.5) formé sur le bras oscillant (26.1) est concave, dans un plan de coupe perpendiculaire à l'axe de révolution. 4. Filtration mechanism according to any one of the preceding claims, characterized in that the raceway (26.5) formed on the oscillating arm (26.1) is concave in a cutting plane perpendicular to the axis of revolution.
5. Mécanisme de filtration selon l'une quelconque des revendications précédentes, caractérisé en ce que le chemin de roulement (26.6) formé sur le volant d'inertie oscillant (22) est tourné radialement vers l'intérieur. 5. Filtration mechanism according to any one of the preceding claims, characterized in that the raceway (26.6) formed on the oscillating flywheel (22) is rotated radially inwards.
6. Mécanisme de filtration selon l'une quelconque des revendications précédentes, caractérisé en ce que le chemin de roulement (26.6) formé sur le volant d'inertie oscillant (22) est concave, dans un plan de coupe perpendiculaire à l'axe de révolution. 6. Filtration mechanism according to any one of the preceding claims, characterized in that the raceway (26.6) formed on the oscillating flywheel (22) is concave in a cutting plane perpendicular to the axis of revolution.
7. Mécanisme de filtration selon l'une quelconque des revendications précédentes, caractérisé en ce que le chemin de roulement (26.6) formé sur le volant d'inertie oscillant (22), le chemin de roulement (26.5) formé sur le bras oscillant (26.1) et le corps roulant (26.4) sont tels que dans la position de référence, le corps roulant (26.4) est dans une position d'éloignement maximal par rapport à l'axe de révolution (100). 7. Filtration mechanism according to any one of the preceding claims, characterized in that the raceway (26.6) formed on the oscillating flywheel (22), the raceway (26.5) formed on the oscillating arm ( 26.1) and the rolling body (26.4) are such that in the reference position the rolling body (26.4) is in a position of maximum distance from the axis of revolution (100).
8. Mécanisme de filtration selon l'une quelconque des revendications précédentes, caractérisé en ce que le bras oscillant (26.1) pivote par rapport à l'organe à amortir (15, 114) autour d'un axe de pivotement (200), le corps roulant (26.4) ayant un axe de rotation parallèle à l'axe de pivotement (200). Filtration mechanism according to one of the preceding claims, characterized in that the oscillating arm (26.1) pivots with respect to the damping member (15, 114) about a pivot axis (200), the rolling body (26.4) having an axis of rotation parallel to the pivot axis (200).
9. Mécanisme de filtration selon l'une quelconque des revendications précédentes, caractérisé en ce que le corps roulant (26.4) est un rouleau. 9. Filtration mechanism according to any one of the preceding claims, characterized in that the rolling body (26.4) is a roller.
10. Mécanisme de filtration selon l'une quelconque des revendications précédentes, caractérisé en ce que le bras oscillant (26.1) comporte une face d'appui (26.8) venant en appui contre le volant d'inertie oscillant (22) sous l'effet d'une déformation élastique du bras oscillant (26.1) lorsque la vitesse de rotation de l'organe à amortir (15, 114) dépasse un seuil donné. 10. Filtering mechanism according to any one of the preceding claims, characterized in that the oscillating arm (26.1) comprises a bearing face (26.8) bearing against the oscillating flywheel (22) under the effect an elastic deformation of the oscillating arm (26.1) when the speed of rotation of the member to be damped (15, 114) exceeds a given threshold.
1 1 . Chaîne cinématique de transmission comportant un mécanisme de filtration selon l'une quelconque des revendications précédentes interposé entre un vilebrequin d'un moteur à combustion interne tournant autour de l'axe de révolution (100) et une boîte de transmission, la chaîne cinématique de transmission comportant en outre un organe d'entrée cinématiquement (12) interposé entre le vilebrequin et l'organe à amortir (15, 114), l'organe à amortir (15, 114) constituant un organe secondaire tournant autour de l'axe de révolution (100) par rapport à l'organe d'entrée (12). 1 1. Transmission kinematic chain comprising a filter mechanism according to any one of the preceding claims interposed between a crankshaft of an internal combustion engine rotating about the axis of revolution (100) and a gearbox, the transmission kinematic chain further comprising a kinematically input member (12) interposed between the crankshaft and the member to be damped (15, 114), the member to be damped (15, 114) constituting a secondary member rotating about the axis of revolution (100) with respect to the input member (12).
12. Chaîne cinématique de transmission selon la revendication précédente, caractérisé en ce qu'elle comporte des éléments de rappel élastique (16, 17) pour rappeler l'organe secondaire (15, 114) vers une position angulaire de référence par rapport à l'organe d'entrée (12). 12. Kinematic transmission chain according to the preceding claim, characterized in that it comprises elastic return elements (16, 17) for biasing the secondary member (15, 114) to an angular reference position relative to the input member (12).
PCT/EP2015/059943 2014-05-12 2015-05-06 Mechanism for filtering torque fluctuations WO2015173086A1 (en)

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Publication number Priority date Publication date Assignee Title
EP3385568A4 (en) * 2016-03-16 2018-12-19 Aisin Aw Co., Ltd. Vibration damping device and design method therefor
WO2019223831A1 (en) * 2018-05-23 2019-11-28 Schaeffler Technologies AG & Co. KG Ring pendulum device

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US2387776A (en) * 1939-05-19 1945-10-30 Salomon Francois Marie Bernard Oscillation reducing device
WO2014033043A1 (en) * 2012-08-27 2014-03-06 Bayerische Motoren Werke Aktiengesellschaft Centrifugal pendulum

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2387776A (en) * 1939-05-19 1945-10-30 Salomon Francois Marie Bernard Oscillation reducing device
WO2014033043A1 (en) * 2012-08-27 2014-03-06 Bayerische Motoren Werke Aktiengesellschaft Centrifugal pendulum

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3385568A4 (en) * 2016-03-16 2018-12-19 Aisin Aw Co., Ltd. Vibration damping device and design method therefor
US10480615B2 (en) 2016-03-16 2019-11-19 Aisin Aw Co., Ltd. Vibration damping device and method of designing the same
WO2019223831A1 (en) * 2018-05-23 2019-11-28 Schaeffler Technologies AG & Co. KG Ring pendulum device

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FR3020849B1 (en) 2017-07-07
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