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
  • F16F15/14—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
• • 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
  • F16F15/12—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
  • F16F15/133—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 using springs as elastic members, e.g. metallic springs
  • F16F15/134—Wound springs
  • F16F15/13469—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
  • F16F15/13476—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
  • F16F15/13484—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs
  • F16F15/13492—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs the sets of springs being arranged at substantially the same radius

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.
• connection between the connecting rod and the oscillating arm is not a simple pivot connection, but preferably a rolling connection implementing a roller rolling simultaneously on two cylindrical tracks of larger diameter, one secured to the connecting rod and the other swing arm, which allows a desired functional game in the link.
• the articulated modules are opposed by centrifugal effect to 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 the square of the rotation speed of the mass of inertia linked to the crankshaft.
• a blocking value for example 2500 rpm
• the mechanism performs its function satisfactorily, but generates unwanted noise when the engine stops, or as soon as the speed of rotation is no longer sufficient to impose the position of the oscillating arms by centrifugal effect. Indeed, at these low speeds, the play in the connection between connecting rod and articulated arm leaves an undesirable freedom of movement in the mechanism.
• This disadvantage can be overcome by replacing the roller connection with a pivot connection, but at the cost of greater fatigue of the mechanism, which reduces its service life.
• the invention aims to overcome the disadvantages of the state of the art and reduce noise when stopping a filter mechanism torque variations.
• 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 pivoting arm pivoting about a pivot connected to the member to be damped and a kinematic connecting member between the oscillating arm and the oscillating flywheel.
• the oscillating arm comprises a zone of contact with the kinematic connecting member and a heel, located on either side of the pivot, the heel being located opposite a stop track cooperating with the heel to limit pivoting. swing arm in a direction bringing the contact zone closer to the axis of revolution. This avoids the oscillating arm, when the speed of the member to be dampened to a halt and the centrifugal forces become insufficient, come beat by generating an undesirable noise.
• the abutment track is preferably formed on the oscillating flywheel. According to one embodiment, the abutment track is shaped to further limit the pivoting of the oscillating arm in the direction closer to the contact zone of the axis of revolution when the oscillating flywheel is in the position. reference relative to the member to be damped only when the oscillating flywheel is located in another position relative to the member to be damped.
• the torque fluctuation filtering mechanism further comprises a radial abutment located opposite a radial abutment zone of the oscillating arm to limit angular pivoting of the contact zone of the oscillating arm. swinging arm radially away from the axis of revolution.
• the radial abutment comes into contact with the radial abutment zone only when the mechanism exceeds a speed threshold of revolution about the axis of revolution, for example due to an elastic deformation of the oscillating arm, the pivot or a piece of the link module.
• the contact between the radial abutment and the radial abutment zone is obtained when the oscillating flywheel is in the reference position relative to the member to be damped.
• the pivot is located between the heel and the radial abutment zone.
• the contact zone may be located between the radial abutment zone and the pivot.
• the radial stop is fixed relative to the member to be damped.
• the radial stop may be fixed relative to the oscillating flywheel.
• angular stops for limiting the angular displacement of the flywheel oscillating relative to the member to be damped.
• These angular stops preferably comprise at least a first angular abutment integral with the member to be damped cooperating with a second angular abutment integral with the oscillating flywheel.
• one of the angular stops constitutes the radial abutment. It can also be provided that the abutment track is shaped so as to form at least one of the angular abutments.
• the kinematic connecting member may comprise a connecting rod. It may also comprise a connecting rolling body, preferably a roller, rolling on a raceway formed on the oscillating arm and on a raceway formed on the oscillating flywheel. In this latter configuration, the limitation of pivoting of the oscillating arm in a direction bringing the contact zone closer to the axis of revolution is also useful in order to avoid an escape of the rolling body.
• FIG. 1 is a diagrammatic view of a torque converter incorporating a filtering mechanism 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 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.
• 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 is 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 an isometric view of a filter mechanism incorporating an oscillating mechanism according to another embodiment of the invention;
• Figure 13 is a sectional view of the mechanism of Figure 12;
• Figure 14 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 organ input 12 and the output member 14, connected to the input member 12 by a first elastic member 16 of rigidity K1 and the output member 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 around 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 filtering mechanism 10 is constituted by a subassembly comprising a pair of guide washers 12.1, 12.2 fixed to one another 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 exit 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, alternately 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 with three pins 15.31 fixed on the annular support piece.
• 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.
• the 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 raceway 26.6 formed on the oscillating flywheel 22.
• the race 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 rotated radially towards it. inside.
• the two raceways 26.5, 26.6 are concave in cross section perpendicular to the axis of revolution 100 with different constant radii of curvature.
• 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 raceway 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.
• FIG. 9 there is a plane perpendicular to the axis of revolution 100 which cuts the oscillating arm 26.1, the connecting rolling body 26.4 and the oscillating flywheel 22.
• the rolling body of Link 26.4 is radially interposed between the raceways 26.5, 26.6 formed on the oscillating arm 26.1 and on the oscillating flywheel 22 in said plane.
• 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.
• each connection module 26 is then in a median position relative to the raceways 26.5, 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 contact between the roller and the raceway formed on the oscillating arm and by a point of contact between the roller 26.4 and the race 26.5 formed on the oscillating flywheel 22, this axis 300 being perpendicular to the two paths of bearing 26.5, 26.6, at the two points of contact.
• This reference position is therefore a position of equilibrium.
• the roll is in the equilibrium position described above, and the resulting stresses at level 26.5 and 26.6, which are themselves radial, do not give rise to any 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.
• the oscillating mechanism 30 passes through a relatively short phase during which the centrifugal forces are no longer sufficient to ensure the support of the oscillating arms 26.1 on the rollers 26.4.
• the angular pivoting of the oscillating arms 26.1 in the clockwise direction in the figures is, however, limited by the heels 26.9 which abut on the curved tracks 26.10, which prevents the rollers 26.1 from escaping their housings.
• the amplitude of pivoting of the swing arms 26.1 is controlled, which also avoids unwanted noise when passing at a standstill.
• 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 cleaned 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.
• FIGS. 12 and 13 is illustrated another embodiment of a torque fluctuation filtration mechanism 10 according to the block diagram of Figure 1.
• this embodiment differs from the previous only by the structure of the connection modules 26 between the oscillating flywheel 22 and the phasing member 15 to produce the oscillating mechanism 30.
• three connecting modules 26 are arranged at 120 ° from each other around the revolution axis 100.
• Each link module 26, illustrated more precisely in FIGS. 12 and 13, comprises an oscillating arm 26.1 hinged to the annular support piece 15.3 by means of a pivot 26.2 for pivoting around a pivot axis parallel to the axis of revolution 100, and a link 26.40 connecting the oscillating arm 26.1 to the oscillating flywheel 22.
• the connecting rod 26.40 is mounted by a pivot link 26.41 to the flywheel, and by a rolling bearing 26.42 to the swing arm, between the pivot 26.2 and a mass extension 26.7 of the swingarm.
• This rolling connection 26.42 confers a limited degree of freedom in the positioning of the axis of rotation between the connecting rod 26.40 and the oscillating arm 26.1. It consists of a roller 26.421 rolling on a concave raceway 26.422 formed by a cylindrical cavity of the connecting rod 26.40 and on a concave raceway 26.423 formed by a cylindrical cavity of the oscillating arm 26.1, the bearing tracks 26.422 and 26.423 having a radius of curvature greater than that of the roller 26.421.
• a portion of the swing arm 26.1 also forms a bearing face 26.8. Opposite the rolling connection 26.42 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 opposes the pivoting of the swingarm in a clockwise direction.
• the connecting 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 radial equilibrium position of the connecting rod.
• the link 26.40 When the link 26.40 is radial, it generates no return torque between the oscillating flywheel 22 and the phasing member 15, and the system is in an equilibrium position.
• 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 rod 26.40 and therefore the resultant of the forces transmitted by the connecting member 26 to the phasing member 15, generating a restoring torque to the equilibrium position, which increases with the amplitude of the angular deflection and the square of the rotational speed about 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 mechanism passes through a relatively short phase during which the centrifugal forces are no longer sufficient to ensure the positioning of the roller in the rolling connection 26.42 between 26.40 connecting rod and swingarm 26.1.
• the angular pivoting of the oscillating arm 26.1 in the clockwise direction in the figures is, however, limited by the heel 26.9 which bears on the curved track 26.10, which makes it possible to control the amplitude of the pivoting of the oscillating arms 26.1 and avoids unwanted noise. at the stop.
• the oscillating mechanism 30 can also be used in other applications requiring filtration of a rotating member.
• FIG 14 a transmission linkage 1 of a motor vehicle having a dry clutch 5 located between a crankshaft 2 and a gearbox input shaft 3. Downstream of the clutch in the drive train 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 transmission box 3. An elastic member 16 is interposed between the input member and the output member so as to work during angular positioning fluctuations between primary flywheel 12 and secondary flywheel 114.
• An oscillating mechanism 30 according to the invention, comprising an oscillating flywheel 22 connected to the secondary flywheel 114 by modules of link 26, allows attenuation of vibrations at low speed of the secondary flywheel 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.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Acoustics & Sound (AREA)
• Aviation & Aerospace Engineering (AREA)
• Mechanical Engineering (AREA)
• Mechanical Operated Clutches (AREA)
• Electrophotography Configuration And Component (AREA)

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Citations (3)

• 2014
  • 2014-05-12 FR FR1454221A patent/FR3020850B1/fr not_active Expired - Fee Related
• 2015
  • 2015-05-06 DE DE112015002215.5T patent/DE112015002215T5/de not_active Withdrawn
  • 2015-05-06 WO PCT/EP2015/059945 patent/WO2015173087A1/fr active Application Filing

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