• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
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    • 专利摘要:
    Device (1) for damping torsional oscillations, comprising: - a support (2) able to move in rotation about an axis (X), - at least one pendulum body (3) comprising: a first and a second pendular mass (5) axially spaced relative to each other and movable relative to the support (2), the first pendulum mass (5) being arranged axially on a first side (4) of the support (2 ) and the second pendulum mass (5) being disposed axially of a second side (4) of the support (2), and at least one connecting member (6) of the first and second pendulum masses (5) matching said masses and secured to the latter by press fit, each pendulum mass (5) having an opening (7) in which the connecting member (6) is force-fitted, this opening having a radially outer edge (47) and a radially inner edge (40), and the connecting member (6) having a radial edge interior (30) and a radially outer edge (31), said radially outer edge (31) extending between two angular ends (33) being each defined by an ear (34) of the connecting member (6), each pendulum mass (5) exerting on the connecting member (6) force-fitted in its opening (7): - a force (F3, F4) on each lug (34) of the connecting member (6), and a force (F1, F2) via a nose (42) projecting radially and carried by the radially inner edge (40) of the opening (7) or by the radially inner edge (30) of the connecting member (6).
    公开号:FR3031369A1
    申请号:FR1550079
    申请日:2015-01-07
    公开日:2016-07-08
    发明作者:Roel Verhoog；Franck Cailleret
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    [0001] The present invention relates to a device for damping torsional oscillations, in particular for a motor vehicle transmission system. In such an application, the torsion oscillation damping device may be integrated with a torsion damping system of a clutch capable of selectively connecting the heat engine to the gearbox, in order to filter the vibrations due to motor acyclisms. Alternatively, in such an application, the torsion oscillation damping device may be integrated with a friction disk of the clutch or with a hydrodynamic torque converter. Such a device for damping torsional oscillations conventionally employs a support and one or more pendular bodies movable relative to this support, the displacement relative to the support of the pendular bodies being guided by rolling members cooperating with one another. part with bearing tracks secured to the support, and secondly with rolling tracks secured to the pendular bodies. Each pendulum body comprises for example two pendular masses riveted together. The rivet thus forms a connecting member for the two pendulum masses. This rivet has two heads protruding axially beyond each pendulum mass away from the support, thus generating a certain size.
    [0002] There is a need to make it possible to secure two pendular masses of a pendulum body in a manner that overcomes the aforementioned drawback. A first aspect of the invention aims to meet this need and achieves it with the aid of a device for damping torsional oscillations, comprising: a support able to move in rotation about a axis, - at least one pendular body comprising: first and second pendular masses axially spaced relative to each other and movable relative to the support, the first pendular mass being disposed axially on a first side of the support and the second pendulum mass being arranged axially on a second side of the support, and at least one connecting member of the first and second pendular masses matching said masses and secured to the latter by force-fitting, each pendulum mass having an opening in which the connecting member is force-fitted, this opening having a radially outer edge and a radially inner edge, and the connecting member presentan a radially inner edge and a radially outer edge, said radially outer edge of the connecting member extending between two angular ends being each defined by an ear of the connecting member, each pendulum mass exerting on the link fitted with force in its opening: - a force on each ear of the connecting member, and - a force via at least one nose protruding into the opening and carried by one of the radially inner edge of the opening and the radially inner edge of the connecting member. In such a device, the forces exerted by each pendulum mass on the connecting member serve to ensure the maintenance of the connecting member in the pendulum body without the binding member being subjected to constraints that may affect its integrity. At least three contact zones can exist between a pendulum mass and the connecting member. The protruding nose may be carried by the radially inner edge of the opening. This nose then protrudes radially into the opening. Alternatively, it may be a nose carried by the radially inner edge of the body of the sense of the present application: - "axially" means "parallel to the axis of rotation of the support", - "radially "Means" along an axis belonging to a plane orthogonal to the axis of rotation of the support and intersecting that axis of rotation of the support ", -" angularly "or" circumferentially "means" around the axis of rotation of the support ", and -" solidarity "means" rigidly coupled ". The two pendular masses can have exactly the same shape and, from a pendulum mass to another of the same pendulum body, the forces exerted by the similarly shaped parts of the pendulum masses on the connecting member can have the same direction.
    [0003] The connecting member may be secured to each pendulum mass only by force fitting, that is to say without any additional securing means such as welding or riveting. This reduces the number of operations required to assemble the pendulum body. Alternatively, the connecting member is secured to each pendulum mass by force fitting and other securing means, for example welding or riveting. One or more rivets are for example arranged through the connecting member, each rivet extending from one pendulum mass to the other. Two noses may be borne by the radially inner edge of the opening or by the radially inner edge of the connecting member, each nose then allowing the exercise of a force by the pendulum mass on the connecting member fitted in force in the opening.
    [0004] Four contact zones then exist between a pendulum mass and the connecting member. The forces exerted by a pendulum mass on the connecting member can then be distributed satisfactorily. The two noses may be positioned relative to each other so that a bending force is exerted by the pendulum mass on the connecting member via said nose. The radially inner edge of the connecting member, respectively of the opening, is for example substantially plane and, in a plane orthogonal to the axis of rotation of the support, the distance between the two noses borne by the radially inner edge of the opening, respectively borne by the radially inner edge of the connecting member, may be between 30% and 100%, preferably between 50% and 90% of the length of the radially inner edge of the connecting member, respectively of said radially inner edge of the opening. Alternatively, the two noses may be positioned relative to each other so that a compressive force is exerted by the pendulum mass on the connecting member via said nose. The radially inner edge of each opening may have two radially protruding noses in the opening, said noses succeeding one another as one moves along said radially inner edge of the opening, and each pendulum mass exerts on the link forcibly engaged in its opening: - a force on each ear of the connecting member, and - a force via each nose of its radially inner edge on the radially inner edge of the connecting member. In all of the above, when two noses are carried by the radially inner edge of the opening, each ear and the opening of each pendulum mass can be configured so that, in a plane orthogonal to the axis of rotation , the force exerted on each ear has a direction intersecting the radially inner edge of the opening at a point between the two nose of the latter. Such a direction of the forces can allow the exercise by the latter of a controlled compression of the connecting member. As a variant, in all the foregoing, when two noses are borne by the radially inner edge of the connecting member, each ear and the opening of each pendulum mass can be configured so that, in a plane orthogonal to the axis of rotation, the force exerted on each ear has a direction intersecting the radially inner edge of the connecting member at a point between the two nose of the latter. Each ear and the opening of each pendulum mass are for example such that the direction of these forces leads to an optimal case.
    [0005] In a particular case, each ear and the opening of each pendulum mass are configured so that, in a plane orthogonal to the axis of rotation, the force exerted on each ear has a direction intersecting the radially inner edge of the opening, respectively the radially inner edge of the connecting member, at a point located substantially equidistant from each nose. In a variant, the pendulum mass exerts no forces on the connecting member via its lugs, but the radially outer edge of the opening projects towards the inside of the opening and this projection comes into contact with the radially outer edge of the connecting member and at a distance from each ear, this contact corresponding to the exercise of a force by the pendular mass on the connecting member. According to this variant, one or more radial noses may be provided on the radially inner edge of the opening or on the radially inner edge of the connecting member, so that several contact zones between the pendulum mass and the link exist: a contact zone associated with the projection formed on the radially outer edge of the opening and a contact zone associated with each nose.
    [0006] In all the foregoing, each connecting member can be made in one piece, for example by striking. Alternatively, as already mentioned, each connecting member may be made of several parts, one of the parts being formed for example by rivets contributing to securing the connecting member to the pendulum body. Each opening may extend along an axis and the connecting member may have, along this axis, successively in this opening: an end portion forming a free space with the lateral wall of the opening arranged opposite this end portion of the connecting member, and - another portion resting against the side wall of the opening disposed opposite this other portion of the connecting member, the free space may have a size him to accommodate all or part of the material of the pendulum mass or the other portion of the connecting member moved during the force fitting of the connecting member in this opening. The displaced material may have been torn off from the pendulum mass or the other portion of the connecting member, thereby forming chips. As a variant, the displaced material may remain integral with the pendulum mass or the other portion of the connecting member, this displaced mass leading to a deformation of the pendulum mass or of the other portion of the connecting member by compared to its shape before fitting into force. This deformation corresponds for example to the presence of a bead on the pendulum mass or on the connecting member. The existence of the free space, dimensioned to accommodate all or part of the material thus displaced, reduces or even eliminates the presence of burrs on the damping device at the end of the force fitting of the body of link. Such a damping member devoid of burrs is thus better suited to the quality requirements of a customer. Before forcing the connecting member into force in the opening, the latter notably has a dimension transverse to the axis of the opening which is greater than the corresponding transverse dimension of the opening, so that theoretical encroachment area of the connecting member on the side wall of the opening exists. Due to the existence of this theoretical encroachment zone, the material displacement mentioned above occurs. The size of the free space can then be chosen according to the size of the theoretical encroachment zone, so that the free space can accommodate all or part of the displaced material. The volume of the free space is for example proportional to the volume of the theoretical encroachment zone and the coefficient of proportionality can be chosen to take account of the fact that all the material contained in the theoretical encroachment zone is not displaced. . The coefficient of proportionality is for example between 0.05 and 0.2. The free space can be obtained by means of a chamfer formed in each edge of said end portion of the connecting member facing the side wall of the opening. Such a chamfer can be obtained in a simple way. Other forms of the end portion of the connecting member for providing such a free space are however possible. The axis of fitting of the connecting member may be coincident with the axis of the opening. The connecting member extends for example between two axial ends, each axial end being disposed in an opening of one of the pendular masses and each axial end comprising: the end portion forming with the side wall of the opening free space and the other portion in contact with said side wall. In all the foregoing, the damping device may comprise at least one rolling member cooperating on the one hand with a running track secured to the support, and on the other hand with a running track secured to the pendulum body to guide the displacement of the pendular body relative to the support. The raceway defined by the pendulum body can then be defined by the radially outer edge of the connecting member. In this case, the first aspect of the invention above can make it possible to compress the runway integral with the pendular body in a controlled manner, particularly when the two aforementioned noses are positioned relative to one another. so that a bending force is exerted on the connecting member by said nose. The life of the raceway defined by the connecting member can thus be extended. Such a bending force may for example make it possible to maintain the shape of this rolling track constant, independently of the stresses experienced by said runway during operation. The raceway defined by the radially outer edge of the connecting member may have a concave shape in a plane orthogonal to the axis of rotation. Alternatively, the raceway defined by the radially outer edge of the connecting member may have several distinct shapes, as will be seen later.
    [0007] The pendulum body may comprise two connecting members, each connecting member being force-fitted in the first and in the second pendulum mass, each connecting member defining a raceway for a running member specific to said connecting member, each member connecting link further cooperating with a raceway defined by the support for guiding the displacement of the pendular body relative to the support.
    [0008] In all the foregoing, each rolling member is for example a roll of circular section orthogonal to the axis of rotation of the support. The axial ends of the roll may be devoid of a thin annular flange. The roller is for example made of steel. In all of the above, the shape of the rolling tracks may be such that the pendulum bodies are only displaced relative to the support in translation about a fictitious axis parallel to the axis of rotation of the support. As a variant, the shape of the rolling tracks may be such that the pendular bodies are displaced with respect to the support both: in translation around a notional axis parallel to the axis of rotation of the support and also in rotation around the center of gravity of said pendular body, such a movement being again called a "combined movement" and disclosed, for example, in the application DE 10 2011 086 532. The rolling tracks secured to the support and the running tracks integral with the pendulum body, and cooperating with the same rolling member may be at least partly radially opposite, that is to say that there are orthogonal planes to the axis of rotation in which these raceways both extend. The device may comprise at least one interposition piece of which at least a portion is axially arranged between the support and a pendulum mass of the pendular body. Such an interposition piece can thus limit the axial displacement of the pendular body relative to the support, thus avoiding axial shocks between said parts, and thus wear and unwanted noises, especially when the support and / or the pendulum mass are made of metal. Several interposition pieces, for example in the form of pads, may be provided. The interposition pieces are in particular made of a damping material, such as plastic or rubber.
    [0009] The interposition pieces are for example carried by the pendular bodies. The interposition pieces can be positioned on a pendular body so that there is always at least one interposition piece at least a portion of which is axially interposed between a pendulum mass and the support, whatever the positions relative to the support and said mass when moving relative to the support of the pendulum body. In all of the above, the support may or may not be made in one piece. In all the above, the device may comprise at least one abutment damping member simultaneously coming into contact with the support and the pendular body in relative positions of the support and the pendulum body. Said relative positions may comprise at least one of: the rest position of the device, the abutment position against the support of the pendulum body at the end of a displacement in the trigonometric direction of this pendulum body from the rest position , and the stop position against the support of the pendulum body at the end of a displacement in the non-trigonometric direction of the pendulum body from the rest position.
    [0010] For the purposes of the present application, the device for damping torsional oscillations is at rest when it does not filter the torsional oscillations. The abutment damping member may have elastic properties for damping shocks related to the contact between the support and the pendulum body. This damping is then allowed by a compression of the abutment damping member.
    [0011] The abutment damping member is for example elastomer or rubber. The abutment damping member is advantageously carried by the pendulum body, being for example arranged radially inwardly with respect to all or part of the radially inner edge of the connecting member. The device comprises for example several pendular bodies, for example a number between two and eight, including three or six pendulous bodies. All these pendular bodies may succeed one another circumferentially. The device can thus comprise a plurality of planes orthogonal to the axis of rotation in each of which all the pendular bodies are arranged. According to a second aspect, the subject of the invention is also a device for damping torsional oscillations, comprising: a support able to move in rotation about an axis, at least one pendular body comprising: first and second pendular masses axially spaced relative to one another and movable relative to the support, the first pendular mass being disposed axially of a first side of the support and the second pendular mass being disposed axially of a second side of the support, and at least one connecting member of the first and second pendular masses matching said masses, the connecting member being secured to each of the pendulum masses only by force fitting.
    [0012] All or some of the features mentioned above with respect to the first aspect of the invention apply to this second aspect of the invention. The invention further provides, according to a third aspect, a device for damping torsional oscillations, comprising: a support able to move in rotation about an axis, at least one pendular body comprising: first and second pendular masses axially spaced relative to one another and movable relative to the support, the first pendular mass being disposed axially of a first side of the support and the second pendular mass being disposed axially of a second side of the support, and at least one connecting member of the first and second pendulum masses matching said masses, the connecting member being secured to each of the pendulum masses by press fitting, each pendulum mass having an opening extending along an axis and the connecting member having, along this axis, successively in this opening: - an end portion providing a free space with the a side wall of the opening disposed facing this end portion of the connecting member, and - another portion resting against the side wall of the opening disposed opposite this other portion of the connecting member , the free space having a size allowing it to accommodate all or part of the material of the pendulum mass or the other portion of the connecting member moved during the force fitting of the connecting member in this opening.
    [0013] All or some of the features mentioned above with respect to the first aspect of the invention apply to this third aspect of the invention. More particularly, according to this third aspect of the invention, before force fitting of the connecting member in the opening, the latter may have a transverse dimension with respect to the axis of the opening which is greater than the dimension corresponding cross-section of the opening, so that a theoretical encroachment zone of the connecting member on the side wall of the opening exists. Due to the existence of this theoretical encroachment zone, the material displacement mentioned above occurs. The size of the free space can then be chosen according to the size of the theoretical encroachment zone, so that the free space can accommodate all or part of the displaced material. The volume of the free space is for example proportional to the volume of the theoretical encroachment zone and the coefficient of proportionality can be chosen to take account of the fact that all the material contained in the theoretical encroachment zone is not displaced. . The coefficient of proportionality is for example between 0.05 and 0.2. The free space can be obtained by means of a chamfer formed in each edge of said end portion of the connecting member facing the side wall of the opening. Such a chamfer can be obtained in a simple way. Other forms of the end portion of the connecting member for providing such a free space are however possible. The axis of fitting of the connecting member may be coincident with the axis of the opening. The connecting member extends for example between two axial ends, each axial end being disposed in an opening of one of the pendular masses and each axial end comprising: the end portion forming with the side wall of the opening free space and the other portion in contact with said side wall. According to a fourth aspect, the subject of the invention is also a device for damping torsional oscillations, comprising: a support able to move in rotation about an axis, at least one pendular body comprising: first and second pendular masses axially spaced relative to one another and movable relative to the support, the first pendular mass being disposed axially of a first side of the support and the second pendular mass being disposed axially of a second side of the support, and at least one connecting member of the first and second pendular masses matching said masses and integral with the latter, - at least one rolling member interacting on the one hand with a running track secured to the support and on the other hand with a running track integral with the pendulum body so as to guide the displacement of the pendular body relative to the support, and - at least one damping member for the pendular body relative to the support, the running track integral with the pendulum body having: a first portion of first shape on which the rolling member rolls when it moves in a first displacement range from a rest position, and a second portion, of second form different from the first shape, on which the rolling member rolls when it moves beyond the first displacement range in a second displacement range during which the abutment damping member comes into contact with both the support and the pendulum body.
    [0014] All or some of the features mentioned above with respect to the first aspect of the invention apply to this fourth aspect of the invention. The first form may be chosen to allow the torsional oscillations to be filtered by the pendulum body when the rolling member rolls along the first portion of the raceway, which is not necessarily the case with the second form. . The action of the abutment damping member to damp the contact between the support and the pendular body thus does not affect the filtering by the pendulum body of the torsional oscillations since it occurs when the rolling member rolls. along the second portion of the raceway. This fourth aspect of the invention thus makes it possible for the stop damping function not to be done to the detriment of the filtering function. The integral running track of the pendular body is advantageously defined by an edge, in particular the radially outer edge, of the connecting member. In this case, the second portion of this raceway includes each circumferential end of the raceway.
    [0015] The first portion of the raceway defined by the edge of the connecting member extends on either side of the position occupied by the rolling member in the rest position of the device, and this first portion may have a length measured along said first portion of the track between 70% and 90% of the total length of this track, this total length being measured between the two circumferential ends of this track. In a plane orthogonal to the axis of rotation of the support, the first portion of the raceway may have a concave shape and the second portion of the raceway may have a convex shape, such shapes being particularly adapted to the function filtering for the first portion of the raceway and the damping function by the thrust damping member for the second portion of the raceway. According to a fifth aspect, the subject of the invention is also a component for a transmission system of a motor vehicle, the component being in particular a double damping flywheel, a hydrodynamic torque converter or a friction disk, comprising a device for damping of torsional oscillations according to any of the first to fourth aspects of the invention. The support of the torsion oscillation damping device can then be one of: - a web of the component, - a guide washer of the component, - a phasing washer of the component, or - a separate support of said web, said guide ring and said phasing washer. The invention will be better understood on reading the following description of examples of implementation thereof and on examining the appended drawing, in which: FIG. 1 schematically and partially shows a device torsion oscillation damping, - Figure 2 shows a detail of Figure 1, - Figure 3 shows a connecting member force-fitted in the opening of a pendulum mass according to a first variant of a first aspect of the invention, - Figure 4 shows the connecting member of Figure 3 when it cooperates with a rolling member, - Figure 5 is a view similar to Figure 4 according to a second variant of the first aspect of FIG. 6 is a view similar to FIG. 4 according to a third variant of the first aspect of the invention; FIG. 7 is a view similar to FIG. 3 according to another aspect of the invention; FIG. 8 is a view similar to FIG. In yet another aspect of the invention, FIG. 9 partially and schematically shows a further aspect of the invention, and FIGS. 10 and 11 show schematically and in part a further aspect of the invention. There is shown in Figure 1 a damping device 1 of torsional oscillations. The damping device 1 is of the pendulum oscillator type. The device 1 is particularly suitable for equipping a motor vehicle transmission system, being for example integrated with a component not shown of such a transmission system, this component being for example a double damping flywheel, a hydrodynamic torque converter or a friction disc. This component can be part of a propulsion system of a motor vehicle, the latter comprising a thermal engine including three or four cylinders.
    [0016] In Figure 1, the device 1 is at rest, that is to say, it does not filter the torsional oscillations transmitted by the propulsion chain due to the acyclisms of the engine. In known manner, such a component may comprise a torsion damper having at least one input element, at least one output element, and circumferentially acting resilient return members which are interposed between said input and output elements. . For the purposes of the present application, the terms "input" and "output" are defined with respect to the direction of torque transmission from the engine of the vehicle to the wheels of the latter. The device 1 comprises in the example under consideration: a support 2 able to move in rotation about an axis X, and a plurality of pendular bodies 3 movable relative to the support 2. In the example considered, six bodies pendulum 3 are provided, being evenly distributed around the periphery of the X axis. The support 2 of the damping device 1 may consist of: - an input element of the torsion damper, - an element of output or an intermediate phasing element disposed between two sets of spring of the damper, or - an element rotatably connected to one of the aforementioned elements and distinct from the latter, then being for example a support specific to the device 1.
    [0017] The support 2 is in particular a guide washer or a phasing washer. In the example considered, the support 2 generally has a ring shape having two opposite sides 4 which are here planar faces. As can be seen in FIG. 1, each pendulum body 3 comprises in the example under consideration: two pendulum masses 5, each pendulum mass 5 extending axially opposite one side 4 of the support 2, and two link 6 securing the two pendulum masses 5. The connecting members 6, also called "spacers", are in the example considered angularly offset.
    [0018] Each connecting member 6 extends partly in a window 9 formed in the support 2. In the example considered, the window 9 defines a free space inside the support, this window being delimited by a closed contour 10. As will be seen later, the connecting member 6 is secured to each pendulum 5 being force-fitted into an opening 7 formed in said pendulum mass 5.
    [0019] The device 1 also comprises, in the example under consideration, rolling members 11, visible in FIG. 2 for example, and guiding the displacement of the pendular bodies 3 with respect to the support 2. The rolling members 11 are here rollers having a section circular cross.
    [0020] In the example described, the movement relative to the support 2 of each pendulum body 3 is guided by two rolling members 11, each of them cooperating with one of the connecting members 6 of the pendulum body 3. Each bearing 11 cooperates on the one hand with a raceway 12 defined by the support 2, and which is here formed by a portion of the contour 10 of the window 9 formed in the support, and on the other hand with a rolling track 13 defined by the pendulum body 3, and which is here formed by a portion of the outer contour of the connecting member 6. The rolling track 13 is here concave shape. More specifically, each rolling member 11 interacts radially internally with the rolling track 13 and at the radially outer level with the rolling track 12 during its movement relative to the support 2 and the pendulum body 3, being for example only requested in compression between the rolling tracks 12 and 13 mentioned above. As can be seen in FIG. 2, the device 1 can also comprise abutment damping members 20 able to come into simultaneous contact with a connecting member 6 and with the support 2 in certain relative positions of the support 2 and pendular bodies 3, such as the positions of abutment at the end of a deflection from the rest position. Each abutment damping member 20 is here integral with a pendular body 3, being mounted on each pendulum mass and arranged to be interposed radially between the connecting member 6 and the contour 10 of the opening 9. Although not shown, the device 1 may further comprise interposition pieces arranged axially between each pendulum mass 5 and the support 2, each interposition piece being for example attached to the pendulum mass 5. As already mentioned, each link 6 is, according to the examples described with reference to FIGS. 3 to 9, force-fitted into an opening 7 of a pendulum mass 5. Each axial end of a connecting member 6 is thus held in an opening 7 of a pendulum mass 5. Each connecting member may have a section orthogonal to the axis of rotation X substantially constant support when moving along this axis X.
    [0021] In the example considered, the connecting member 6 comprises a radially inner plane edge and a radially outer edge 31, a part of which defines the rolling track 13 already mentioned. The radially outer edge 31 is concave in the plane of FIG. 3. This radially outer edge 31 extends, in planes orthogonal to the axis of rotation X, between two angular ends 33 which are each defined by an ear 34 of the connecting member 6.
    [0022] The two lugs 34 diverge from one another from a core 35 of the connecting member 6 when one moves radially away from the axis of rotation X of the support 2. The heart 35 of the link corresponds as can be seen in Figures 3 and 4 to the portion of the connecting member 6, the radially outer edge defines the hollow of the concavity formed by the radially outer edge 31.
    [0023] The lugs 34 of the connecting member 6 may be images of one another with respect to a plane P containing an axis parallel to the axis of rotation X of the support 2. The connecting members 6 of FIGS. 7 are only secured to each pendulum mass 5 by force fit. The connecting members 6 of Figures 3 to 6 cooperate with each pendulum 5 so as to compress the raceway 13 defined by the connecting member 6 in a controlled manner. As can be seen in Figure 3, the radially inner edge 40 of the opening 7 may have radial noses 42 protruding into the opening 7. In Figure 3, two radial noses 42 are provided and these radial noses 42 are spaced from each other by a distance d between 50% and 90% of the length L of the radially inner edge 30 of the connecting member 6, this length L of the edge 30 being measured in an orthogonal plane to the axis of rotation X of the support 2. Such spacing between the two nose allows them to exert a combined flexural force on the connecting member 6. This bending force can be used to close the raceway 13, to open, or to ensure that the shape of the raceway 13 remains constant regardless of the constraints applied thereto. The pendulum mass 5 thus exerts two forces Fi and F2 oriented substantially radially outwards on the connecting member 6 when the latter is fitted into the opening 7. As shown in FIG. 3, the pendulum mass 5 can exert two other forces F3 and F4 on the connecting member 6, so that there are then four contact zones between the pendulum mass 5 and the connecting member 6. Each ear 34 is here subjected to a force F3 or F4 of the part of the pendulum mass 5. Part of the contour of the ear 34 thus comes into contact with part of the contour of the opening 7 and this contact corresponds to the exercise of the force F3 or F4 by the pendulum 5 .
    [0024] As shown in FIG. 3, these forces exerted on the lugs 34 may have a direction intersecting the radially inner edge 30 of the connecting member 6 between the two radial noses 42. As can be seen in FIG. 4, when the support is rotated at high speeds, the rolling member 11 also exerts a compressive force F5 on the rolling track 13, this force F5 adding to the forces Fi to F4 exerted by the pendulum mass 5 on the connecting member 6. The connecting member 6 and the pendulum mass 5 of FIG. 5 differ from those just described with reference to FIGS. 3 and 4 by the arrangement of the radial noses 42. The radial noses 42 are here always offset along the radially inner edge 40 but a distance d which is this time between 10% and 40% of the length L of the radially inner edge 30 of the connecting member 6. The radial noses 42 can here exercise in a combined way e a compression force on the connecting member 6. The connecting member 6 and the pendulum 5 of Figure 6 differ from those just described with reference to Figures 3 to 5 by the number of nose radial radial formed on the radially inner edge 40 of the opening 7. A single radial nose 42 is in this example provided and it exerts a force F12 on a substantially central area of the radially inner edge 30 of the connecting member 6. Similarly to what has already been described with reference to FIG. 3, forces F3 and F4 are exerted by the pendulum 5 on each lug 34 of the connecting member 6. The connecting member 6 and the pendulum mass 5 of Figure 7 differs from those just described with reference to Figures 3 to 6. Indeed, the shape of the opening 7 is different. The radially outer edge 47 of this opening 7 defines a radial projection 48 in the opening 7 and this radial projection 48 comes into contact with the connecting member 6 when the latter is fitted into the opening 7 of the pendulum mass 5. Due to this contact, a force F12 directed substantially radially inwards is exerted by the radially outer edge 47 of the opening 7 on the connecting member 6. This force replaces the forces F3 and F4 exerted on each ear 34 of the connecting member of Figures 3 to 6. The connecting member 6 then undergoes a bending force under the combined effect of forces Fi, F2 and F34.
    [0025] The connecting member and the pendulum 5 of Figure 8 differ from those just described in that the connecting member 6 is no longer secured to each pendulum mass 5 only by force fitting. Several rivets 50 can thus be used. In the example described, two rivets 50 are provided. The radially inner edge 40 of the opening 7 may then be devoid of radial noses and the distance between the rivets 50 may be substantially equal to the distance d of FIG. 3. The forces F 1 and F 2 mentioned above are then exerted at the level of FIG. each rivet 50. The loading of the connecting member 6 then occurs when the rolling member 11 applies a force against the raceway 13. will now be described with reference to Figure 9 another aspect of the The invention may or may not be combined with the device described with reference to FIGS. 3 to 8.
    [0026] FIG. 9 is a view along IX of the device of FIG. 3. As can be seen, the opening 7 extends along an axis Y which is parallel to the axis of rotation X of the support 2. 6 has an axial end 60 received in the opening 7, this end 60 having previously been force-fitted into the opening 7 along an axis of fitting parallel to the Y axis of the opening 7. The end axial 60 of the connecting member 6 comprises, as can be seen in Figure 9, an end portion 61 which is the first introduced into the opening 7 at the press fitting, and another portion 62 introduced into the opening 7 following the end portion 61. As can be seen in FIG. 9, at the end of the force fit, the end portion 61 can come to the same level as the outer wall 63 of the pendular mass 5 opposite the wall 64 of the pendulous mass 5 which is axially opposite the support 2. As shown in Figure 9, the connecting member 6 has before fitting, at the ears 34, lateral edges 65 which extend beyond the side wall 66 of the opening 7. A zone theoretical encroachment Z1 of the connecting member 6 on the side wall 66 of the opening 7 exists as well. This zone Z1 is hatched in FIG. 9. A free space Z2, also hatched in FIG. 9, is also provided between the end portion 61 of the connecting member and the wall 66 of the opening 7. This free space is here obtained by chamfering at least one of the lateral edges 65 at the end portion 61 of the connecting member. Due to this chamfer, a reserve of space is provided locally between the connecting member 6 and the side wall 66 of the opening, and this reserve can accommodate all or part of the material of the pendulum mass 5 which is displaced due to the friction with the portion 62 during force-fitting in the opening 7 of this portion 62. The volume of the free space Z2 is in the example described proportional according to a proportionality coefficient of between 0.05 and 0.2 to the volume of the Zl encroachment zone.
    [0027] As shown in FIG. 9, at the end of the press fitting, the lateral edges 65 of the end portion 61 are spaced from the lateral wall 66 of the opening 7 while the lateral edges 65 of the other portion 62 come into contact with the side wall 66 of the opening 7. The free space Z2 is totally, or only partially, occupied by the material of the pendulum mass 5 displaced when the press fitting is in force. connecting member 6, this material may or may not include chips. As shown in FIG. 9, another chamfer 69 may be formed in the wall 64 of the pendulum mass 5. This other chamfer 69 can promote the introduction of the axial end 60 of the connecting member 6 into the opening 7.
    [0028] A further aspect of the invention that may or may not be combined with what has been described with reference to FIGS. 3 to 9 will now be described with reference to FIGS. 10 and 11. As can be seen, the rolling track 13 is always defined by the radially outer edge of the connecting member 6, but this running track 13 has, from the rest position PO that the rolling member 11 occupies when the device 1 is at rest, different successive forms. The running track 13 thus has: a first portion 70 of first shape on which the rolling member 11 rolls when it moves from the rest position PO in a first displacement range, and - a second portion 71, of second form different from the first form, on which the rolling member 11 rolls when it moves beyond the first range of displacement in a second range of displacement. In this example, each abutment damping member 20 which is integral with the connecting member 6 is made of elastomer or rubber and it ensures damping of the abutment of the connecting member 6 against the support 2 by compressing himself. The compression of the abutment damping member 20 occurs while the rolling member 11 rolls along the second portion 71 of the raceway 13. In this example and in a plane orthogonal to the X axis the first portion 70 is concave while the second portion 71 is convex, such shapes favoring the filtering of torsional oscillations as long as the rolling member 11 rolls along the first portion 70. As can be seen on 10, the length of the first portion 70, measured from the rest position PO to the beginning of the second portion 71, is for example greater than 80% of the length of the tread measured between the position PO and the end position P1 reached by the rolling member 11 when the connecting member 6 abuts against the support 2, the abutment damping member 20 then being compressed. As shown in FIG. 11, the first portion 70 is for example defined by a constant radius R1 while the second portion 71 is defined by another constant radius R2.
    [0029] The invention is not limited to the examples which have just been described.
    权利要求:
    Claims (12)
    [0001]
    REVENDICATIONS1. Device (1) for damping torsional oscillations, comprising: - a support (2) able to move in rotation about an axis (X), - at least one pendulum body (3) comprising: a first and a second pendular mass (5) axially spaced relative to each other and movable relative to the support (2), the first pendulum mass (5) being arranged axially on a first side (4) of the support (2 ) and the second pendulum mass (5) being disposed axially of a second side (4) of the support (2), and at least one connecting member (6) of the first and second pendulum masses (5) matching said masses and secured to the latter by press fit, each pendulum mass (5) having an opening (7) in which the connecting member (6) is force-fitted, this opening having a radially outer edge (47) and a radially inner edge (40), and the connecting member (6) having a radial edge interior (30) and a radially outer edge (31), said radially outer edge (31) extending between two angular ends (33) being each defined by an ear (34) of the connecting member (6), each pendulum mass (5) exerting on the connecting member (6) force-fitted in its opening (7): - a force (F3, F4) on each lug (34) of the connecting member (6), and a force (F1, F2) via at least one nose (42) projecting into the opening (7) and carried by one of the radially inner edge (40) of the opening (7) and the radially edge interior (30) of the connecting member (6).
    [0002]
    2. Device according to claim 1, the connecting member (6) being secured to each pendulum mass (5) only by force fitting.
    [0003]
    3. Device according to claim 1 or 2, two noses (42) being borne by the radially inner edge (40) of the opening (7) or by the radially inner edge (30) of the connecting member (6). , each nose (42) allowing the exercise of a force by the pendulum mass (5) on the connecting member (6) force-fitted in the opening (7).
    [0004]
    4. Device according to claim 3, the two noses (42) being positioned relative to each other so that a bending force is exerted by the pendulum mass (5) on the connecting member (6) via said noses (42).
    [0005]
    5. Device according to claim 3, the two noses (42) being positioned relative to each other so that a compression force is exerted by the pendulum mass (5) on the connecting member (6) via said noses (42).
    [0006]
    6. Device according to any one of claims 3 to 5, each lug (34) and the opening (7) of each pendulum mass (5) being configured so that, in a plane orthogonal to the axis of rotation (X), the force (F3, F4) exerted on each lug (34) has a direction intersecting the radially inner edge (40) of the opening (7) or the radially inner edge (30) of the link (6) at a point between the two noses (42) of the latter.
    [0007]
    7. Device according to the preceding claim, each lug (34) and the opening (7) of each pendulum mass (5) being configured so that, in a plane orthogonal to the axis of rotation (X), the the force (F3, F4) exerted on each lug (34) has a direction intersecting the radially inner edge (40) of the opening (7) or the radially inner edge (30) of the connecting member (6) in one point substantially equidistant from each nose (42).
    [0008]
    8. Device according to any one of claims 3 to 7, the radially inner edge (40) of each opening (7) having two nose (42) projecting radially into the opening (7), said nose (42) is succeeding when moving along said radially inner edge (40) of the opening, and each pendulum mass (5) exerting on the connecting member (6) force-fitted in its opening (7): - a force (F3, F4) on each lug (34) of the connecting member (6), and - a force (F1, F2) via each nose (42) of its radially inner edge (40) on the radially inner edge (42) of the connecting member (6).
    [0009]
    9. Device according to any one of the preceding claims, comprising at least one rolling member (11) cooperating on the one hand with a raceway (12) integral with the support, and on the other hand with a running track ( 13) integral with the pendulum body.
    [0010]
    10. Device according to claim 9, the raceway (13) defined by the pendular body being defined by the radially outer edge (31) of the connecting member (6).
    [0011]
    11. Device according to any one of the preceding claims, the pendulum body (3) comprising two connecting members (6), each connecting member (6) being force-fitted into the first (5) and the second (5). ) pendular mass, each connecting member defining a raceway (13) for a running member (11) specific to said connecting member (6), each connecting member cooperating further with a raceway (12) defined by the support for guiding the displacement of the pendulum body (3) relative to the support (2).
    [0012]
    12. Device (1) for damping torsional oscillations, comprising: - a support (2) able to move in rotation about an axis (X), - at least one pendulum body (3) comprising: a first and second pendulum masses (5) axially spaced relative to one another and movable relative to the support (2), the first pendulum mass (5) being arranged axially on a first side (4) of the support (2) and the second pendulum mass (5) being disposed axially of a second side (4) of the support (2), and at least one connecting member (6) of the first and second pendulum masses (5). matching said masses, the connecting member (6) being secured to each of the pendulum masses only by force fitting.
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    同族专利:
    公开号 | 公开日
    CN105757165B|2022-01-28|
    CN105757165A|2016-07-13|
    US20160195164A1|2016-07-07|
    FR3031369B1|2017-10-20|
    US9958028B2|2018-05-01|
    CN114110087A|2022-03-01|
    引用文献:
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    FR2982335A1|2011-11-07|2013-05-10|Valeo Embrayages|PENDULUM OSCILLATOR TYPE FILTRATION DEVICE HAVING AN IMPROVED GUIDE SYSTEM|
    EP2687749A1|2012-07-20|2014-01-22|Valeo Embrayages|Torsional damper with pendular mass|
    WO2014012835A1|2012-07-20|2014-01-23|Valeo Embrayages|Damping system of pendular oscillator type comprising an inbuilt guidance device|FR3069298A1|2017-07-24|2019-01-25|Valeo Embrayages|CLUTCH DEVICE, IN PARTICULAR FOR A MOTOR VEHICLE|FR2718813B1|1994-04-14|1996-07-12|Valeo|Shock absorber flywheel, especially for a motor vehicle.|
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    US8739523B2|2008-06-02|2014-06-03|Schaeffler Technologies AG & Co. KG|Rotary vibration damper with centrifugal force pendulum|
    DE112011100857B4|2010-03-11|2018-12-13|Schaeffler Technologies AG & Co. KG|Centrifugal pendulum device|
    FR2981714B1|2011-10-19|2013-11-01|Valeo Embrayages|PENDULUM OSCILLATOR TYPE DAMPING SYSTEM WITH IMPROVED GUIDE DEVICE|
    DE102013208430A1|2012-05-16|2013-11-21|Schaeffler Technologies AG & Co. KG|centrifugal pendulum|FR3013415B1|2013-11-15|2016-05-27|Valeo Embrayages|SIMPLIFIED PULSE TORSION DAMPING DEVICE|
    FR3036762B1|2015-06-01|2017-06-02|Valeo Embrayages|TORSION OSCILLATION DAMPING DEVICE|
    FR3044059B1|2015-11-25|2017-11-24|Valeo Embrayages|PENDULAR DAMPING DEVICE|
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    法律状态:
    2016-02-01| PLFP| Fee payment|Year of fee payment: 2 |
    2016-07-08| PLSC| Publication of the preliminary search report|Effective date: 20160708 |
    2017-01-31| PLFP| Fee payment|Year of fee payment: 3 |
    2018-01-31| PLFP| Fee payment|Year of fee payment: 4 |
    2020-01-31| PLFP| Fee payment|Year of fee payment: 6 |
    2021-01-28| PLFP| Fee payment|Year of fee payment: 7 |
    2022-01-31| PLFP| Fee payment|Year of fee payment: 8 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1550079A|FR3031369B1|2015-01-07|2015-01-07|TORSION OSCILLATION DAMPING DEVICE|FR1550079A| FR3031369B1|2015-01-07|2015-01-07|TORSION OSCILLATION DAMPING DEVICE|
    US14/988,963| US9958028B2|2015-01-07|2016-01-06|Device for damping torsion oscillations, notably for a motor vehicle transmission system|
    CN202111457465.6A| CN114110087A|2015-01-07|2016-01-07|Torsional vibration damping device|
    CN201610009910.5A| CN105757165B|2015-01-07|2016-01-07|Torsional vibration damping device|
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