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
  • F16F15/133—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
  • F16F15/1333—Spiral springs, e.g. lying in one plane, around axis of rotation
• • 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
  • F16F15/1338—Motion-limiting means, e.g. means for locking the spring unit in pre-defined positions
• • 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
  • F16F2230/00—Purpose; Design features
  • F16F2230/0052—Physically guiding or influencing
  • F16F2230/0064—Physically guiding or influencing using a cam
• • 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
  • F16F2232/00—Nature of movement
  • F16F2232/02—Rotary
• • 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
  • F16F2234/00—Shape
  • F16F2234/06—Shape plane or flat
• • 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
  • F16F2236/00—Mode of stressing of basic spring or damper elements or devices incorporating such elements
  • F16F2236/08—Torsion
• • 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
  • F16F2238/00—Type of springs or dampers
  • F16F2238/02—Springs
  • F16F2238/024—Springs torsional

Definitions

• the invention relates to a torsion damper for equipping a torque transmission device.
• the invention relates more particularly to the field of transmissions for a motor vehicle.
• the torsion dampers comprise an input member and an output member rotatable about a common axis of rotation and resilient damping means for transmitting the torque and damping rotational acyclisms between the input member. and the output element.
• Such torsion dampers equip including double damping flywheels (DVA) and / or friction clutch, in the case of a manual or robotic transmission, or locking clutches, also called “lock-up” clutches, equipping hydraulic coupling devices, in the case of an automatic transmission.
• DVA double damping flywheels
• locking clutches also called “lock-up” clutches
• equipping hydraulic coupling devices in the case of an automatic transmission.
• the document FR3000155 illustrates a torsion damper comprising elastic damping means each formed of two resilient blades mounted on the input element and each cooperating with a respective cam follower mounted on the output element.
• the blades and cam followers are arranged such that, for angular displacement between the input member and the output member, on either side of a relative angular position of rest, the follower of cam moves along the blade and, in doing so, exerts a bending force on the resilient blade.
• the resilient blade exerts on the cam follower a restoring force which tends to bring the input and output elements to their angular position of rest. The bending of the resilient blade thus makes it possible to damp the vibrations and irregularities of rotation between the input element and the output element while ensuring the transmission of torque.
• One aspect of the invention is based on the idea of solving the drawbacks of the prior art by proposing an elastic blade torsion damper which is particularly effective and in which the elastic blade is subjected to weaker forces. constraints.
• the invention provides a torsion damper for a torque transmission device comprising:
• blade damping means for transmitting torque and damping rotational acyclisms between the first member and the second member, the blade damping means comprising:
• the blade damping means comprises two flexible blade regions radially offset from one another in a radial direction, a free space radially separating said two regions of flexible blade.
• such a blade arrangement is likely to provide a blade surface with which the bearing element with a larger circumferential length cooperates.
• This additional circumferential length of the surface of the blade with which the support element cooperates allows a greater angular displacement between the elements, which allows a decrease in the stiffness of the blade and consequently a better damping of the motor acyclisms. .
• such a torsion damper may have one or more of the following characteristics:
• the blade is arranged to deform in a plane perpendicular to the axis of rotation X.
• one of the flexible blade regions is located between the axis of rotation and the other of the flexible blade regions.
• said at least one blade has a radially movable free distal end such that the radial distance between the axis of rotation of said free distal end varies as a function of the angular displacement between the first and second members.
• the angular sector along which the two flexible blade regions are radially offset from each other extends over at least 1 °, for example over at least 5 °, preferably at least 10 °, in particular at least 30 ° °.
• said at least one blade comprises a portion for fixing the blade on said first or second element and an elastic portion, the elastic portion comprising the free distal end of said at least one blade, said at least one support element being arranged to cooperate with the elastic portion of said at least one blade.
• the elastic portion has an inner and outer strand connected by a bend, the inner strand developing from the attachment portion to the elbow and the outer strand developing circumferentially from the elbow to the free distal end, the internal strand having one of the two blade regions flexibly and radially offset from the damping means and the outer strand having the other of the two blade regions flexible and radially offset from the damping means.
• the fixing portion develops circumferentially and has a thickness in a radial direction less than the thickness of the outer strand of the elastic portion.
• the fixing portion develops circumferentially over a length less than the length of the outer strand of the elastic portion.
• the fixing portion develops circumferentially over a length less than 50% of the length of the outer strand, preferably less than 30%.
• said at least one support element is arranged radially outside the outer strand of said at least one blade.
• the outer strand extends circumferentially over at least 45 ° and can extend circumferentially up to 180 ° in a bent state of the blade corresponding to a maximum angular displacement between the first element and the second element °.
• the blade damping means comprises two elastically deformable blades integral with one of said first and second elements and two bearing elements carried by the other of said first and second elements, the support elements being respectively arranged to cooperate with one and the other of the two elastically deformable blades,
• each blade has two flexible blade regions radially offset from each other, a free space radially separating said flexible blade regions from each of the blades.
• the blade damping means comprises two elastically deformable blades integral with one of said first and second elements and two bearing elements carried by the other of said first and second elements, the bearing elements being respectively arranged to cooperate with one and the other of the two elastically deformable blades and each blade comprises one of the two flexible blade regions radially offset from one another.
• the elastically deformable blades are symmetrical with respect to the axis of rotation X.
• each elastically deformable blade has an internal clearance, the clearance of a blade having a radius of curvature greater than the radius of curvature of an outer surface of the other blade so that said outer surface of the other blade can fit into the clearance.
• the elastically deformable blades are attached independently to the first or second element.
• the elastic portion comprises a cam surface and said at least one support member comprises a cam follower arranged to cooperate with the cam surface.
• the cam follower is a roller rotatably mounted on the respective first or second element by means of a rolling bearing.
• the invention also relates to a torque transmission element, in particular for a motor vehicle, comprising a torsion damper mentioned above.
• such a transmission element may have one or more of the following characteristics: the transmission element comprises two aforementioned torsion dampers arranged in series.
• the transmission element comprises two aforementioned torsion dampers arranged in parallel.
• One aspect of the invention is based on the idea of reducing the stiffness of the damping means in order to allow better damping of the acyclisms.
• One aspect of the invention is based on the idea of increasing the maximum angular deflection between the input element and the output element.
• One aspect of the invention starts from the idea to reduce stress concentration areas on a spring blade.
• One aspect of the invention is to provide a blade torsion damper subject to acceptable stresses when transmitting high torque.
• An object of the invention is to provide a torsion damper for filtering quality acyclisms.
• An object of the invention is to provide an elastic blade having a large length.
• An object of the invention is to provide a blade having a cam surface of great length.
• FIG. 1 is a front view of a double damping flywheel illustrating the general operation of a torsion damper, in which the secondary flywheel is shown, in a transparent manner, so as to display the damping means.
• Figure 2 is a sectional view of the double damping flywheel of Figure 1, according 11-ll.
• Figure 3 is a perspective view of the double damping flywheel of Figure 1.
• Figure 4 is a perspective view of the dual damping flywheel of Figures 1 to 3, wherein the secondary flywheel is shown, partially broken away and disassembled from the primary flywheel.
• Figure 5 is a schematic view of an elastically deformable blade illustrating the deflection of the blade during an angular deflection between a first element and a second element in a direct direction.
• Figure 6 is a schematic view of an elastically deformable blade illustrating the deflection of the blade during an angular movement between a first element and a second element in a retro direction.
• Figure 7 is a schematic view of a torsion damper in the rest position comprising a damping means according to one embodiment of the invention.
• Figure 8 is a schematic view of the torsion damper of Figure 7 in an angular displacement position between the first member and the second member.
• the terms "external” and “internal” as well as the “axial” and “radial” orientations will be used to designate, according to the definitions given in the description, elements of the torsion damper.
• the "radial” orientation is directed orthogonally to the axis (X) of rotation of the elements of the torsion damper determining the "axial” orientation and, from the inside towards the outside while moving away of said axis, the "circumferential” orientation is directed orthogonally to the axis of rotation of the torsion damper and orthogonal to the radial direction.
• an element described as circumferentially developing is an element whose component develops in a circumferential direction.
• the double damping flywheel 1 comprises a primary flywheel 2, intended to be fixed at the end of a crankshaft of an internal combustion engine, not shown, and a secondary flywheel 3 which is centered and guided on the primary flywheel 2 by means of a rolling ball bearing 4.
• the secondary flywheel 3 is intended to form the reaction plate of a clutch, not shown, connected to the input shaft of a gearbox.
• the primary flywheels 2 and secondary 3 are intended to be mounted movable about an axis of rotation X and are, moreover, rotatable relative to each other about said axis X.
• the primary flywheel 2 comprises a radially inner hub 5 supporting the rolling bearing 4, an annular portion 6 extending radially from the hub 5 and a cylindrical portion 7 extending axially, on the opposite side to the motor, from the outer periphery of the annular portion 6.
• the annular portion 6 is provided, on the one hand, with screw holes 8 for fixing , intended for fixing the primary flywheel 2 on the crankshaft of the engine and, secondly, for passing rivets 9 for fixing a damping means on the primary flywheel 2.
• the primary flywheel 2 door , on its outer periphery, a ring gear 10 for driving in rotation of the primary flywheel 2, using a starter.
• the hub 5 of the primary flywheel has a shoulder 1 1 serving to support an inner ring of the rolling bearing 4 and which retains said inner ring towards the motor.
• the secondary flywheel 3 has on its inner periphery a shoulder 12 serving to support an outer ring of the rolling bearing 4 and retaining said outer ring in the opposite direction to the motor.
• the secondary flywheel 3 comprises a flat annular surface 13, turned on the opposite side to the primary flywheel 2, forming a bearing surface for a friction lining of a clutch disc, not shown.
• the secondary flywheel 3 has, close to its outer edge, pads 14 and orifices 15 for mounting a clutch cover.
• the secondary flywheel 3 further comprises orifices 16, arranged vis-à-vis the orifices formed in the primary flywheel 2, and for the passage of the screws 8, when mounting the double damping flywheel 1 on the crankshaft.
• the primary flywheels 2 and secondary 3 are coupled in rotation by a damping means.
• this damping means comprises two resilient blades 17a, 17b mounted integral in rotation with the primary flywheel 2.
• the elastic blades 17a, 17b are carried by a ring body 18 provided with holes for the passage of the fastening rivets 9 to the primary flywheel 2.
• the annular body 18 further comprises orifices 19 for the passage of the screws 8 for fixing the double damping flywheel 1 to the nose of the crankshaft.
• the two resilient blades 17a, 17b are symmetrical with respect to the axis of rotation X of the clutch disc.
• the elastic blades 17a, 17b have a cam surface 20 which is arranged to cooperate with a cam follower, carried by the secondary flywheel 3.
• the resilient blades 17a, 17b have a curved portion extending substantially circumferentially. The radius of curvature of the curved portion and the length of this curved portion are determined according to the desired stiffness of the elastic blade 17a, 17b.
• the elastic blade 17a, 17b may, as desired, be made in one piece or be composed of a plurality of lamellae arranged axially against each other.
• the cam followers are rollers 21 carried by cylindrical rods 22 fixed on the one hand to the secondary flywheel 3 and on the other hand to a web 23.
• the rollers 21 are rotatably mounted on the cylindrical rods 22 around a axis of rotation parallel to the axis of rotation X.
• the rollers 21 are held in abutment against their respective cam surface 20 and are arranged to roll against said cam surface 20 during a relative movement between the primary and secondary 2 flywheels 3.
• the rollers 21 are radially disposed outside their respective cam surface 20 so as to radially maintain the resilient blades 17a, 17b when subjected to centrifugal force.
• the rollers 21 are advantageously mounted in rotation on the cylindrical rods by means of a rolling bearing.
• the rolling bearing may be a ball bearing or roller.
• the rollers 21 have an anti-friction coating.
• the cam surface 20 is arranged such that, for an angular displacement between the primary flywheel 2 and the secondary flywheel 3, relative to a relative angular position of rest, the roller 21 moves on the cam surface 20 and, in doing so, exerts a bending force on the elastic blade 17a, 17b.
• the elastic blade 17a, 17b exerts on the roller 21 a return force which tends to bring the primary flywheels 2 and secondary 3 to their relative angular position of rest.
• the resilient blades 17a, 17b are able to transmit a driving torque from the primary flywheel 2 to the secondary flywheel 3 (forward direction) and a resistant torque of the secondary flywheel 3 to the primary flywheel 2 (retro direction).
• FIGS. 5 and 6 The operating principle of a damping means with elastic blades 17a, 17b is detailed in relation with FIGS. 5 and 6.
• a driving motor torque is transmitted from the primary flywheel 2 to the secondary flywheel 3 (forward direction)
• the torque to be transmitted causes a relative movement between the primary flywheel 2 and the secondary flywheel 3 in a first direction (see Figure 5).
• the roller 21 is then moved by an angle with respect to the elastic blade 17a.
• the displacement of the roller 21 on the cam surface 20 causes a flexion of the elastic blade 17a along an arrow ⁇ .
• the elastic blade 17a is shown in solid lines in its angular position of rest and in dashed lines during an angular movement.
• the bending force P depends in particular on the geometry of the elastic blade 17a and its material, in particular its transverse modulus of elasticity.
• the bending force P is decomposed into a radial component Pr and a tangential component Pt.
• the tangential component Pt allows the transmission of the engine torque.
• the elastic blade 17a exerts on the roller 21 a reaction force whose tangential component constitutes a restoring force which tends to bring the primary flywheels 2 and secondary 3 to their relative angular position of rest.
• FIG. 7 represents a schematic view of a torsion damper in the rest position comprising damping means according to one embodiment of the invention.
• the resilient blades 17a, 17b are fastened independently of each other on the secondary flywheel 103.
• the cam followers 121 are fixed on the primary flywheel 102.
• Each blade 17a , 1 17b has a fastening portion 1 18 fixed relative to the secondary flywheel 103 to enable the rotation of the resilient blades 1 17a, 1 17b with the secondary flywheel 103.
• a rolling bearing 104 is mounted between the primary flywheel 102 and the secondary flywheel 103.
• This rolling bearing 104 has an outer ring 127 carried by the secondary flywheel 103 which cooperates with an inner ring 128 carried by the primary flywheel 102.
• the fixing portion 1 18 of the blades 1 17a, 1 17b develops circumferentially around the outer ring 127.
• the inner ring 128 of the rolling bearing ball 104 is carried by the hub 105 of the primary flywheel 102.
• each elastic blade 1 17a, 1 17b is fixed to the secondary flywheel 103 by three rivets 129.
• the three rivets 129 are not aligned. on the same axis. Attaching an elastic blade 1 17a, 1 17b with less than three rivets 129 would not provide a good fixation.
• the fixing of an elastic blade 1 17a, 1 17b with a larger number of rivets 129 would generate either, in the case of rivets 129 of the same dimensions, a problem of space, or, in the case of rivets 129 of lower dimensions, a problem of mechanical resistance.
• the fixing portion 1 18 fixed to the secondary flywheel 103 is extended by an elastic portion 130.
• the elastically deformable portion 130 of the blade 11a is schematically represented by a dotted curve 131 in FIG. 7.
• the elastic portion 130 bears on a radially outer face the cam surface 120 cooperating with the cam follower 121.
• the elastic portion 130 of each elastic blade 1 17a, 1 17b comprises an internal strand 132, a bend 133 and an outer strand 134.
• the inner strand 132 of a blade 1 17a, 1 17b extends the fixing portion 1 18.
• the elbow 133 extends inner strand 132 and outer strand 134 extends elbow 133.
• Internal strand 132 develops circumferentially around outer ring 127 from attachment portion 1 to elbow 133.
• Internal strand 132 being not fixed with the rivets 129 on the secondary flywheel 103, it deforms during an angular displacement between the primary flywheel 102 and the secondary flywheel 103. Thus, the internal strand 133 absorbs a portion of the stresses experienced by the resilient blade 1 17a, 1 17b during this angular deflection.
• the elbow 133 forms an angle of approximately 180 ° so that a first end 135 of the contiguous elbow 133 of the inner strand 132 is located radially between the axis of rotation X and a second end 136 of the contiguous elbow 133 of the outer strand 134
• the elastic blade 1 17a, 1 17b thus has a general shape of a hairpin, one branch of which is formed by the outer strand 134 and the other branch is formed jointly by the fixing portion 1 18 and the internal strand 132.
• the elastic portion 130 has two flexible blade regions radially offset from each other and separated by a void space.
• the outer strand 134 develops circumferentially from the elbow 133 to the free end 137 of the spring blade 17a, 17b.
• the outer strand 134 develops over a circumference of at least 45 ° and up to 180 ° in the bent state of the resilient blade 17a, 17b.
• the cam surface 120 develops on an outer face of the outer strand 134.
• the cam surface 120 develops circumferentially at an angle of about 125 ° to 130 °.
• the cam surface 120 develops circumferentially according to a radius of curvature determined according to the desired stiffness of the resilient blades 11a, 17b. This cam surface 120 may have different radii of curvature depending on the desired point stiffness, in order to allow slope variations of the characteristic curve of the torsion damper, representing the torque transmitted as a function of the angular displacement.
• FIG. 7 The elastic blades 1 17a, 1 17b shown diagrammatically in FIG. 7 are symmetrical with respect to the axis of rotation X.
• Figure 8 is a schematic view of the torsion damper of Figure 7 in an angular displacement position between the primary flywheel and the secondary flywheel.
• the torque to be transmitted causes a relative movement between the primary flywheel 102 and the secondary flywheel 103 in a first direction.
• the rollers 121 are then moved by an angle ⁇ with respect to the elastic blades 1 17a, 1 17b.
• the displacement of the rollers 121 on the cam surfaces 120 causes the resilient blades 17a, 17b to bend.
• the flexion of the resilient blades 17a, 17b causes the approximation on the one hand of the outer strands 134 of the blade 17a, 17b with its attachment portion 18 and, on the other hand, the approach of the free end 137 of one of the blades 1 17a, 1 17b with the elbow 133 of the other of the blades 1 17b, 1 17a.
• these connections must not cause contacts between the outer strand 134 and the fixing portion 1 18 of the blade 1 17a, 1 17b, such contacts generating disturbances in the damping of acyclisms and vibrations.
• the circumferential length of the fixing portion 1 18 is limited so that, in the rest position shown in Figure 7, the fixing portion 1 18 does not develop circumferentially beyond the axis formed by the alignment between the cam follower 121 and the axis of rotation X.
• an end 138 of the fastening portion 1 18 opposite the elastic portion 130 of a blade 1 17a, 1 17b is located between the cam follower 121 corresponding and the axis of rotation X during a maximum angular displacement in the retro direction between the primary flywheel 102 and the secondary flywheel 103, as represented by the axis 143.
• Such a maximum angular movement is for example limited by an end stop having a stop 139 on the primary flywheel 102 facing circumferentially a stop 140 on the secondary flywheel 103.
• the thickness of the fixing portion 1 18 is reduced relative to the thickness of the elastic portion 130, and more particularly to the minus the thickness of the end 138 of the fixing portion 1 18 is reduced relative to the thickness of the elastic portion 130.
• the free end 137 of the blades 1 17a, 1 17b comprises a clearance 141.
• This clearance 141 is formed on an inner face of the outer strand 134.
• the clearance 141 advantageously has a radius of curvature identical or close to the radius of curvature of a portion 142 of the outer face of the elbow 133 of the blades 1 17a, 1 17b.
• each blade 1 17a, 1 17b is close to the elbow 133 of the other blade 1 17b, 1 17a, and the portion 142 of the outer surface of the elbow 133 of each blade 1 17b, 1 17a is housed in the clearance 141 of the other blade 1 17a, 1 17b to delay or even avoid contact.
• the length of the elastic blade 1 17a, 1 17b and the arrangement of the outer strand 134, the elbow 133 and the inner strand 132 of an elastic blade 1 17a, 1 17b allows the transmission of a high torque without risk of degradation of the resilient blades 17a, 17b or loss of cooperation between the cam followers 121 and the cam surfaces 120.
• the blades of the damping means may be independent of one another or linked to one another by a central section.
• torsion damper in the context of a double damping flywheel, but such a torsion damper can be installed on any suitable device.
• torsion dampers can equip the clutch friction, in the case of a manual or robotic transmission, or the locking clutches, also called “lock-up” clutches, equipping hydraulic coupling devices, in the case of an automatic transmission.

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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)

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• 2014
  • 2014-10-01 FR FR1459347A patent/FR3026802B1/fr active Active
• 2015
  • 2015-09-24 JP JP2017517737A patent/JP6630352B2/ja active Active
  • 2015-09-24 WO PCT/EP2015/072018 patent/WO2016050611A1/fr active Application Filing
  • 2015-09-24 EP EP15770510.4A patent/EP3201489A1/de not_active Withdrawn
  • 2015-09-24 US US15/514,978 patent/US20180231097A1/en not_active Abandoned
  • 2015-09-24 CN CN201580053763.5A patent/CN106715956B/zh active Active

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