• 专利附录
  • 专利说明
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    • 专利摘要:
    The invention relates to a dual damping flywheel (1) for a motor vehicle comprising: - a sail fixed to a secondary flywheel by fasteners (17); and - a primary flywheel (2) having a plurality of orifices (18) which are each formed opposite one of said fastening members (17); - a sealing washer (19) which is pressed axially against the primary flywheel (1) and comprises a plurality of openings (24, 46, 49) distributed around the X axis and a plurality of plugs (25) which protrude axially towards the primary flywheel (2) and are each disposed between two adjacent openings (24, 46, 49) of said plurality of openings; said closure washer (19) being able to move from a position of installation of said fasteners in which the openings (24) are each opposite one of said orifices (18) of the primary flywheel (2). ) at a sealing position of the primary flywheel in which the plugs (25) are each engaged in one of said orifices (18) of the primary flywheel (2).
    公开号:FR3039240A1
    申请号:FR1556836
    申请日:2015-07-20
    公开日:2017-01-27
    发明作者:Gianbattista Lanfranco；Benjamin Laporte
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    DOUBLE SHOCK ABSORBER WHEEL COMPRISING A SHUTTER WASHER TO ENSURE THE SEALING OF THE PRIMARY WHEEL
    TECHNICAL FIELD The invention relates to the field of transmissions for a motor vehicle and relates more particularly to a double damping flywheel.
    Technological background
    Explosions engines do not generate a constant torque and exhibit acyclisms caused by explosions succeeding in their cylinders. These acyclisms generate vibrations that are likely to be transmitted to the gearbox and thus generate shocks, noise and noise, particularly undesirable. In order to reduce the undesirable effects of vibrations and to improve the driving comfort of motor vehicles, certain motor vehicle transmissions are equipped with a double damping flywheel.
    A double damping flywheel is for example described in WO2011124805. This double damping flywheel comprises a primary flywheel intended to be fixed at the end of the crankshaft of the engine, a secondary flywheel, coaxial with the primary flywheel, and forming the reaction plate of a clutch device and suitable elastic members. to transmit torque and dampen rotational acyclisms between the primary flywheel and the secondary flywheel. The primary flywheel has a bottom and a lid defining an annular chamber in which are housed the elastic members. Moreover, the dual mass flywheel also has an annular web which is fixed to the secondary flywheel and which is arranged axially between the bottom and the cover of the primary flywheel. The annular web has radial bearing lugs cooperating with the elastic members.
    Fixing the secondary flywheel on the sail is performed after having previously housed the annular web between the cover and the bottom of the primary flywheel. Therefore, in order to allow the riveting of the secondary flywheel on the sail, the bottom of the primary flywheel comprises a plurality of orifices which are arranged facing the rivets and allowing the passage of a crimping tool capable of deforming the end of the rivets to secure them.
    In order to prevent the ingress of water or pollution, which may affect the operation of the double damping flywheel, inside the annular chamber, a plug is fitted into each of the orifices. The plugs are made of a metal sheet and are each force-fitted by means of a press into a respective orifice. The operation of fitting the plugs in the orifices of the primary flywheel is relatively long to implement and involves a significant increase in the manufacturing cycle of a double damping flywheel. In addition, the fitting operation is likely to cause deformations of the primary flywheel due to the press fitting forces exerted by the press. Finally, the geometrical defects which are likely to affect the primary flywheel and / or the plugs are detrimental to the effectiveness of the seal and do not make it possible to ensure reliable fastening of the plugs in the orifices of the primary flywheel.
    Such a double damping flywheel is therefore not fully satisfactory. summary
    An idea underlying the invention is to propose a double damping flywheel of the aforementioned type in which the sealing of the orifices, formed in the primary flywheel to allow the installation of the fastening members of the sail to the secondary flywheel, is ensured by simple way, without damaging the primary flywheel.
    According to one embodiment, the invention provides a double damping flywheel for a motor vehicle comprising: - a primary flywheel and a secondary flywheel movable in rotation relative to each other about an axis X; - A sail attached to the secondary flywheel by fasteners distributed around the X axis; and - resilient members interposed between the primary flywheel and the sail and capable of transmitting torque and damping rotational acyclisms between the primary flywheel and the secondary flywheel; the primary flywheel having a plurality of orifices which are each formed facing one of said fasteners in order to allow the installation of said fasteners; said damping flywheel further comprising a sealing washer which is axially pressed against the primary flywheel and has a plurality of openings distributed around the X axis and a plurality of plugs which project axially towards the primary flywheel and are each disposed between two adjacent openings of said plurality of openings; said closure washer being adapted to rotate about the X axis relative to the primary flywheel and to move axially relative to the primary flywheel in order to move from an installation position of said fasteners in which the openings are each located opposite one of said holes of the primary flywheel and the plugs are pressed against the primary flywheel to a sealing position of the primary flywheel in which the plugs are each engaged in one of said holes of the primary flywheel.
    Thus, it is no longer necessary to perform an operation of fitting the plugs by means of a press, which makes it possible to reduce the manufacturing cycle of the double damping flywheel. In addition, the risk of deformation of the primary flywheel, due to the use of a press to press the plugs, are eliminated.
    Finally, the effectiveness of the seal is less affected by the geometrical defects of the primary flywheel and the risks of separation of the caps of the primary flywheel are excluded.
    According to other advantageous embodiments, such a dual damping flywheel may have one or more of the following features: the sealing washer is pressed axially against a face of the primary flywheel facing the web. the sealing washer comprises at least a first abutment surface which is arranged such that: when the sealing washer is in its installation position of the fasteners, said first abutment surface is able to cooperate with a second abutment surface integral in rotation of the web, during a relative rotation of the secondary flywheel relative to the primary flywheel, so as to move the sealing washer towards its sealing position of the primary flywheel; and that - when the sealing washer is in its position of sealing the primary flywheel, said first abutment surface is not adapted to cooperate with the second abutment surface, during a relative rotation of the secondary flywheel relative to at the primary wheel. Also, the establishment of the sealing washer in its sealing position can be carried out in a simple manner, for example during an operation to control the stiffness of the elastic members of the double damping flywheel, without specific tool. when the sealing washer is in its position of sealing the primary flywheel, the first abutment surface is not in the path of the second abutment surface. the closure washer comprises at least two first abutment surfaces and the double damping flywheel comprises at least two second stop surfaces integral in rotation of the web; the first two abutment surfaces being respectively arranged to cooperate with one of the two second surfaces during the relative rotation of the secondary flywheel with respect to the primary flywheel in a first direction of rotation and with the other of the two second stop surfaces during relative rotation of the secondary flywheel relative to the primary flywheel in a second direction of rotation. the first two abutment surfaces and the two second abutment surfaces are adapted to immobilize the secondary flywheel relative to the primary flywheel in a determined angular position when the sealing washer is in its position of installation of the fasteners. the first abutment surfaces are formed by a flange bordering one of the openings of the sealing washer and projecting axially towards the web, that is to say in a direction opposite to the bottom of the primary flywheel, and the seconds abutment surfaces are formed by the fastener which is opposite said opening of the sealing washer when the sealing washer is in its position of installation of fasteners. the fastening member of the web to the secondary steering wheel is a rivet and the second abutment surface is formed by the rivet head. each of the openings of the sealing washer is bordered by a rim, for example hemi-circular, protruding axially towards the web and forming first abutment surfaces and the fastener opposite each of the openings forming second surfaces of stop adapted to cooperate with the first abutment surfaces formed by the flange during a relative rotation of the secondary flywheel relative to the steering wheel. the fasteners of the sail to the secondary flywheel pass through tabs of the sail bordered by indentations and the sealing washer comprises at least one abutment member projecting axially in one of the notches when the sealing washer is in its mounting position of the fasteners, the stop member forming the first abutment surfaces and the tabs bordering said notch forming the second abutment surfaces. the closure washer comprises a cavity formed on one face of the sealing washer directed towards the web, said cavity being intended to receive a rod of a drive tool capable of moving the sealing washer from its position to installation of the fasteners at its sealing position of the primary flywheel during a relative rotation of the secondary flywheel relative to the primary flywheel, the secondary flywheel and the sail being each equipped with an orifice facing said cavity when the shutter washer is in its installation position, said orifices of the secondary flywheel and the veil being able to allow the passage of the rod of said drive tool. the double damping flywheel further comprises an elastic washer which is, on the one hand, bearing against an annular flange carried by the primary flywheel and, secondly against the sealing washer in order to press the washer of shutter against the primary steering wheel. the spring washer comprises radially outer tabs bearing against the sealing washer, said tabs being received in housings formed in the sealing washer so as to fasten in rotation the spring washer and the sealing washer. the sealing washer comprises a plurality of resilient tongues whose free end bears against an annular flange provided on the primary flywheel so as to press the sealing washer against the primary flywheel. the primary flywheel has a bottom and a hub, the hub having a tubular portion of axial orientation and a radial portion, extending radially outwardly from the tubular portion, said radial portion being fixed against the bottom of the steering wheel primary; the sealing washer being disposed axially between an annular flange formed in an outer edge of the radial portion of the hub and the bottom of the primary flywheel. the sealing washer is axially pressed against a face of the primary flywheel opposite the web. the sealing washer has a circular bulge projecting towards the primary flywheel and extending around each of the plugs. each of the plugs is arranged inside a window formed in the sealing washer and is connected to a border of the window by a plurality of arms. according to one embodiment, the plugs have a dimension slightly greater than that of the holes of the primary flywheel and are force-fitted into the orifices of the primary flywheel when the sealing washer is in its sealing position. the primary flywheel has a bottom, a cover and a cylindrical portion extending axially between the bottom and the cover; the bottom, the lid and the cylindrical portion defining an annular chamber, filled with lubricant, in which the elastic members are housed; the double damping flywheel further comprising two sealing washers fixed to the web and arranged on either side thereof; the sealing washer having an outer zone sandwiched between one of the sealing washers and the bottom of the primary flywheel. In this case, the sealing washer is advantageously made of plastic, which limits the friction between the sealing washer and the bottom of the primary flywheel.
    According to one embodiment, the invention also provides a motor vehicle comprising a double aforementioned damping flywheel.
    BRIEF DESCRIPTION OF THE DRAWINGS The invention will be better understood, and other objects, details, features and advantages thereof will become more clearly apparent from the following description of several particular embodiments of the invention, given solely for the purposes of the invention. illustrative and not limiting, with reference to the accompanying drawings. - Figure 1 is a partial sectional view of a double damping flywheel according to a first embodiment, said double damping flywheel being equipped with a sealing washer shown in a sealing position of the primary flywheel. - Figure 2 is a partial exploded view of the double damping flywheel of Figure 1. - Figure 3 is a detailed view of the double damping flywheel of Figure 1 illustrating the manner in which the sealing washer is pressed against the primary flywheel. - Figure 4 is a front view of the sealing washer. - Figure 5 is a rear view of the sealing washer. - Figure 6 is a sectional view along the axis VI-VI of Figure 3 illustrating the sealing washer, in an installation position of the fastening members of the web to the secondary flywheel. - Figure 7 is a sectional view along the axis VII-VII of Figure 3 illustrating the sealing washer in an installation position of the fasteners. - Figure 8 is a sectional view of the double damping flywheel of Figure 1 before positioning the fastening members of the web to the secondary flywheel. - Figure 9 is a sectional view of the double damping flywheel after positioning the fasteners of the web to the secondary flywheel, the sealing washer being in an installation position of said fasteners. - Figure 10 is a detailed view illustrating the interactions between the sealing washer and the primary flywheel when the sealing washer is in a sealing position of the primary flywheel. 11 is a detailed view illustrating the interactions between the sealing washer and the primary flywheel, according to a second embodiment, when the sealing washer is in a sealing position of the primary flywheel. - Figure 12 is a detailed front view of a sealing washer according to a third embodiment. FIG. 13 is a sectional view of a double damping flywheel according to a fourth embodiment illustrating a driving tool able to move the sealing washer between a position of installation of the fasteners and a position of FIG. sealing of the primary flywheel. - Figure 14 is a front view of the sealing washer of the double damping flywheel of Figure 13. - Figure 15 is a sectional view of a double damping flywheel according to a fifth embodiment. - Figure 16 is a sectional view of a double damping flywheel according to a sixth embodiment. - Figure 17 is a front view of the sealing washer of the double damping flywheel of Figure 16.-Figure 18 is a front view of a sealing washer according to a seventh embodiment. FIG. 19 is a detailed view of one of the resilient tongues of the sealing washer of FIG. 18; FIG. 20 is a perspective view of three quarter-quarter of a double damping flywheel according to an eighth embodiment. . - Figure 21 is a detailed view of the web and a sealing washer of a double damping flywheel according to a ninth embodiment. - Figure 22 is a front view of the sealing washer of the double damping flywheel of Figure 21. - Figure 23 is a partial sectional view of a double damping flywheel according to a tenth embodiment.
    Detailed description of embodiments
    In the description and the claims, 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 double damping flywheel. By convention, the "radial" orientation is directed orthogonally to the X axis of rotation of the double damping flywheel determining the "axial" orientation and, from the inside towards the outside while moving away from said axis, the orientation "circumferential" is directed orthogonally to the axis of the double damping flywheel and orthogonal to the radial direction. The terms "external" and "internal" are used to define the relative position of one element relative to another, with reference to the axis X of rotation of the double damping flywheel, an element close to the axis is thus qualified. internally as opposed to an outer member located radially peripherally. Furthermore, the terms "rear" AR and "front" AV are used to define the relative position of one element relative to another in the axial direction, an element intended to be placed close to the engine being designated by the rear and an element intended to be placed close to the gearbox being designated by before.
    The double damping flywheel 1, shown in FIG. 1, comprises a primary flywheel 2 intended to be fixed at the end of a crankshaft of a combustion engine, not shown, and a secondary flywheel 3 which is intended to form the reaction plate of a clutch device, not shown, connected to the input shaft of a gearbox.
    The primary flywheels 2 and secondary 3 are movable about the axis of rotation X and are furthermore movable in rotation relative to one another about said axis X. The secondary flywheel 3 is centered and guided by rotation on the primary flywheel 1 by means of a bearing 4, such as a rolling bearing as in the embodiment shown. The primary flywheel 2 comprises a central hub 5, radially internal, bearing the centering bearing 4 of the secondary flywheel 3 and a bottom 6 extending radially.
    In the embodiment shown, the hub 5 is an insert which is fixed against the bottom 6 of the primary flywheel 2 by riveting. The hub 5 comprises a tubular portion 10 bearing the centering bearing 4 of the secondary flywheel 3 and a radial portion 7 extending radially outwardly from the rear end of the tubular portion 10. The radial portion 7 is riveted against the bottom 6 of the primary flywheel 2.
    Moreover, the primary flywheel 2 comprises a cylindrical portion 8, represented in FIG. 2, extending axially forwards from the outer periphery of the bottom 6 of the primary flywheel 2 and an annular cover 9, shown in FIG. extending radially and welded to the front end of the cylindrical portion 8. The cover 9 defines with the bottom 6 and the cylindrical portion 8, an annular chamber in which are housed the elastic members 11 of the double damping flywheel 1.
    As shown in FIG. 2, the bottom 6 and the hub 5 have a plurality of orifices 12, 13 regularly distributed around the axis X and intended for the passage of fastening screws making it possible to fix the primary flywheel 2 on the crankshaft a combustion engine. The secondary flywheel 3 also comprises orifices, not shown, facing said orifices 12, 13 of the bottom 6 of the primary flywheel 2 and the hub 5 and allowing the introduction of the screws into the orifices 12, 13, during the assembly of the double flywheel shock absorber 1 on the crankshaft. The primary flywheel 2 carries on its outer periphery a ring gear 14 for driving in rotation of the primary flywheel 2, using a starter.
    The double damping flywheel 1 comprises elastic members 11, partially shown in FIG. 1, which make it possible to transmit a torque between the primary flywheel 2 and the secondary flywheel 3 and to damp the rotational acyclisms. The resilient members 11 are, for example, curved helical springs which are housed in the annular chamber formed in the primary flywheel 2 and circumferentially distributed around the axis X. Each of the elastic members 11 extends circumferentially between two legs. support of a sail 15 secured to the rotation of the secondary flywheel 3 and two support seats carried by the primary flywheel 2. Each support seat carried by the primary flywheel 2 is, for example, constituted by a boss 16, illustrated on 2, formed in the bottom 6 of the primary flywheel 2 and by a boss, not shown, formed in the cover 9. Thus, in operation, each of the resilient members 11 is supported at a first end against a seat of support carried by the primary flywheel 2 and, at a second end, against a support lug carried by the sail 15, so as to ensure the transmission of torque between the primary flywheel 2 and the steering wheel secondary 3.
    The annular chamber in which the elastic members 11 are housed is filled with a lubricating agent, preferably grease, in order to limit the friction between the elastic members 11 and the cylindrical portion 8 of the primary flywheel 2. In order to prevent leakage lubricant towards the outside of the annular chamber, the double damping flywheel 1 is equipped with sealing means disposed on either side of the web 15 and sealing the annular chamber, on the one hand, between the veil 15 and the bottom 6 of the primary flywheel 2, and, on the other hand, between the veil 15 and the cover 9.
    As shown in FIG. 1, the web 15 extends axially between the bottom 6 and the cover 9 of the primary flywheel 2. Moreover, the sail 15 is fixed by a plurality of rivets 17 to the secondary flywheel 3. The rivets 17 are regularly distributed around the axis X. Typically, to allow the assembly of such a dual damping flywheel 1, a first assembly comprising the primary flywheel 2, the web 15 and the resilient members 11 is first preassembled. To do this, the elastic members 11 and the web 15 are arranged against the bottom 6 of the primary flywheel 2 inside its cylindrical portion 8 and the cover 9 is welded against the front end of the cylindrical portion 8. By the subsequently, the secondary flywheel 3 and the sail 15 are fixed to each other. Therefore, in order to allow the riveting operations of the veil 15 on the secondary flywheel 3, it is necessary to allow a crimping tool or bouterrollage, to access the rear end of the rivets 17, via the bottom 6 of the steering wheel primary 2, to allow the deformation of the rivets 17. To do this, the bottom 6 of the primary flywheel 2 has a plurality of orifices 18 which are each arranged opposite a respective rivet 17, when the primary flywheels 2 and secondary 3 are in their relative position of rest, so as to allow the passage of a suitable tool for performing riveting operations.
    In order to ensure the sealing of the primary flywheel 2 at the orifices 18 when the riveting operations are completed, the double damping flywheel 1 is equipped with a sealing washer 19. The sealing washer 19 is arranged around the outer edge of the radial portion 7 of the hub 5 and is held in abutment against the bottom 6 of the primary flywheel 1. To do this, an elastic washer 20 is interposed between an annular flange 21 formed in the outer edge of the radial portion 7 of the hub 5, and the sealing washer 19. The annular flange 21 forms a bearing surface for the spring washer 20 and thus allows it to press the sealing washer 19 rearward against the bottom 6 of the primary flywheel 2 The elastic washer 20 is, for example, of the "Belleville" type. In the embodiment shown, the spring washer 20 bears against the sealing washer 19 by means of a plurality of tabs 22 projecting radially outwardly. The tabs 22 are each received in a housing 23 formed on the front face of the sealing washer 19 so as to secure the spring washer 20 and the sealing washer 19 in rotation. The housing 23 is here delimited by a semi-circular wall. -circular protruding rearward. In addition, fingers extend from the semicircular wall towards the inside of the housing 23 in order to limit the clearances between the tabs 22 of the elastic washer 20 and the sealing washer 19.
    The sealing washer 19 is, for example, made of plastic. The sealing washer 19 has a plurality of openings 24, of circular shape. The openings 24 are identical in number to the number of orifices 18 in the bottom 6 of the primary flywheel 2. In addition, the openings 24 are evenly distributed around the axis X on a diameter corresponding to the implantation diameter of the orifices 18. sealing washer 19 also has a plurality of plugs 25 which are each disposed between two adjacent openings 24. The plugs 25 are also identical in number to the number of orifices 18. Moreover, the plugs 25 are regularly distributed around the X axis to a diameter corresponding to the implantation diameter of the orifices 18. The plugs 25 have a complementary shape. to that of the orifices 18 formed in the primary flywheel 2 and protrude axially rearward, that is to say towards the bottom 6 of the primary flywheel 2. Advantageously, as shown in FIG. 22 of the spring washer 20 exert an axial bearing vis-à-vis each of the plugs 25.
    The sealing washer 19 is adapted to be rotated about the axis X with respect to the primary flywheel 2.
    With reference to FIGS. 3 and 6 to 8, it can be seen that, before riveting operations of the web 15 on the secondary flywheel 3, the sealing washer 19 is arranged in a position, called the installation position of the bodies fixing, in which each opening 24 of the sealing washer 19 is located opposite an orifice 18 of the bottom 6 of the primary flywheel 1. A crimping tool can be introduced through the orifices 18 so as to deform the rear end of the rivets 17, as shown in Figure 9. It is observed in Figure 7, in this mounting position of the fasteners, the plugs 25 are held in abutment against the bottom 6 of the primary flywheel 2 under the action of the axial load exerted by the spring washer 20.
    Moreover, the sealing washer 19 is also able to assume a position, known as sealing position, of the primary flywheel 2, shown in FIG. 1, in which each plug 25 is engaged in a respective orifice 18. To move from its installation position of the fasteners to its sealing position of the primary flywheel 1, the sealing washer 19 must be rotated relative to the primary flywheel 1 about the X axis to a angular position in which the plugs 25 are facing the orifices 18 of the primary flywheel 2 and the axial load exerted by the spring washer 20 axially displaces the sealing washer 19 against the bottom 6 of the primary flywheel 2 so that the plugs 25 engage in the holes 18.
    Advantageously, the sealing washer 19 is equipped with abutment surfaces which are arranged such that, when the sealing washer 19 is in its position of installation of the fixing members, said abutment surfaces are suitable for abut against abutment surfaces integral in rotation of the web 15, during a relative rotation of the secondary flywheel 3 relative to the primary flywheel 2 according to one or other of the directions of rotation. Thus, a relative rotation of the secondary flywheel 3 with respect to the primary flywheel 2 makes it possible to angularly move the sealing washer 19 with respect to the primary flywheel 2 so as to move it from its position of installation of the fasteners towards its position d 2. By way of example, this relative rotation of the primary flywheels 2 and secondary 3 may in particular be carried out during a control operation aimed in particular at qualifying the stiffness of the elastic members 11 and for which a relative rotation flywheels primary 2 and secondary 3 is necessary. This relative rotation of the primary flywheels 2 and secondary 3 can also be performed after the mounting of the double flywheel 1 in the transmission chain. The aforementioned abutment surfaces are also arranged such that, when the sealing washer 19 is disposed in its sealing position of the primary flywheel 2, the abutment surfaces of the sealing washer 19 are not likely to take bearing on the abutment surfaces integral in rotation of the web 15 and that, therefore, the sealing washer 19 remains in its sealing position.
    In the embodiment of Figures 1 to 11, the abutment surfaces are formed by a rim 26 of substantially semicircular shape which borders each of the openings 24 of the sealing washer 19 and which projects forwardly. As shown in FIG. 9, the axial dimension of said flanges 26 is sufficient so that, during a relative rotation between the primary and secondary flywheels 2, the head of each of the rivets 17 bears against one of the flanges 26, so as to rotate the closure washer 19 relative to the primary flywheel 2 towards its sealing position of the primary flywheel 1. The axial dimension of the flanges 26 is however sufficiently small so that the heads of the rivets 17 do not come not in contact with the flanges 26 when the sealing washer 19 is in its sealing position of the primary flywheel 2.
    Note further that a closure washer 19 equipped with such abutment surfaces is also able to ensure a temporary immobilization of the primary flywheels 2 and secondary 3, in a given angular position, when the sealing washer 19 is in its position installation of fasteners. This facilitates the installation of the double damping flywheel in the transmission chain of the vehicle.
    In FIG. 10, it can be seen that the seal is made between the rear face of the sealing washer 19 and the front face of the bottom 6 of the primary flywheel 2. This variant embodiment is advantageous in that, firstly, it makes it possible to overcome the possible geometrical defects of the orifices 18 of the primary flywheel 1 to guarantee the seal and, secondly, it facilitates the positioning of the sealing washer 19 in its sealing position of the primary flywheel 2 because the plugs 25 may in this case have a diameter smaller than that of the orifices 18 of the primary flywheel 2.
    In such a variant, the rear face of the sealing washer 19 is advantageously equipped with circular bulges 27, also shown in Figure 4, projecting rearwardly. Each of the circular bulges 27 encircles a respective cap 25. Such circular bulges 27 make it possible to seal efficiently even when the bottom 6 of the primary flywheel 2 has significant surface irregularities.
    In another variant embodiment illustrated in FIG. 11, the seal is made in a zone of contact between the edges of the orifices 18 of the primary flywheel 2 and the plugs 25. In this case, the size of the plugs 25 is slightly greater than that of the orifices 18 and the axial load exerted by the spring washer 20 must be sufficient to press force each of the plugs 25 in a respective orifice 18, during the movement of the sealing washer 19 towards its position of sealing the primary flywheel 2.
    In Figure 12, a sealing washer 19 according to another embodiment, is partially shown. The structure of such a sealing washer 19 is adapted to the production of a sealing zone between the edges of the orifices 18 and the plugs 25. Each of the plugs 25 is here positioned in the center of a window 28 formed in the closure washer 16. Each plug 25 is connected to the edge of its respective window 28 by four arms 29 defining a spider. Such an arrangement increases the flexibility of the plugs 25, which makes it possible to limit the risks of degradation of the plugs 25 when they are subjected to phenomena of expansion under the effect of high temperatures or when positioning errors of the plugs 25 relative to each other. at the orifices 18 of the primary flywheel 2.
    According to other embodiments, not illustrated, the characteristics of the embodiments described above are combined. Also, according to one embodiment, the rear face of the sealing washer 19 is advantageously equipped with circular bulges 27 encircling each of the plugs 25 while the size of the plugs 25 is such that they are force-fitted into the orifices 18. Such an embodiment embodiment may prove to be relevant to guarantee sealing while, on the one hand, the bottom 6 of the primary flywheel 2 is likely to have significant surface irregularities and that, on the other hand, the orifices 18 are likely to have substantial geometrical defects.
    The embodiment illustrated in Figures 13 and 14, differs from the embodiments described above in that the movement of the sealing washer 19 between its installation position of the fasteners and its sealing position of the primary flywheel is carried out by means of a drive tool 30, shown in FIG. 13. The drive tool 30 comprises at least two rods 31 (only one of which is shown) making it possible to drive the washer shutter 19 relative to the primary flywheel 2. To do this, the sealing washer 19 comprises cavities 32 formed on the front face of the sealing washer 19 which are intended to receive the end of one of the rods. 31 of the training tool. The cavities 32 are, here, formed inside the plugs 25, that is to say formed by the concave face of the plugs 25. Moreover, the web 15 and the secondary flywheel 3 are provided with orifices 33, 34, facing one of the cavities 32, able to be traversed by rod 31 of the drive tool 30.
    Thus, to move the sealing washer 19 from its installation position of the fasteners to its sealing position, the rods 31 of the drive tool 30 are introduced through the orifices 33, 34 of the veil 15. and the secondary flywheel 3 so that the end of each rod 31 is housed in one of the cavities 32 of the sealing washer 19. Thereafter, the drive tool 30 is rotated around of the X axis so as to drive in rotation the secondary flywheel 3, the web 15 and the sealing washer 19, relative to the primary flywheel 1. As in the previous embodiments, when the caps 25 are facing 18 of the primary flywheel 2, the elastic washer 20 exerts on the sealing washer 19 an axial load sufficient to axially move the sealing washer 19 so that the plugs 25 engage inside the orif ices 18.
    Figure 15 illustrates a double damping flywheel 1 according to another embodiment. This double damping flywheel 1 differs from the embodiments described above in that the primary flywheel 2 is a flexible flywheel. In other words, the bottom 6 of the primary flywheel 2 extending radially between the hub 5 and the cylindrical portion 8 is at least partially formed of one or more flexible sheets. Such a primary flywheel 2 makes it possible to dampen excitations, in the axial direction, of the crankshaft. The double damping flywheel 1 differs further from those described above in that the secondary flywheel 3 is not intended to form the reaction plate of a clutch device, but comprises a hub 35 which carries a toothing intended to be coupled to complementary toothing carried by an element of the transmission chain, such as a housing of a double clutch in the oil, not shown. Such a double damping flywheel 1 is equipped with a sealing washer 19 and an elastic washer 20 according to any one of the embodiments described above.
    The double damping flywheel 1, illustrated in relation with FIGS. 16 and 17, differs from those previously described in that the sealing washer 19 also contributes to the sealing of the annular chamber filled with lubricant. The sealing of the annular chamber is here ensured by two sealing washers 36, 37 which are fixed on the web 15, respectively on either side thereof. The two sealing washers 36, 37 are formed by frustoconical plates elastically deformable. At the front, the outer edge of the sealing washer 36 is pressed against the cover 9 of the primary flywheel 2. At the rear, the outer edge of the sealing washer 37 is pressed against a radially outer zone 38 of the shutter washer 19. The radially outer zone 38 of the sealing washer 19 is thus pressed against the bottom 6 of the primary flywheel 2, which makes it possible in particular to seal the annular chamber. Such an arrangement is particularly advantageous in that the sealing washer 19 is made of plastic and thus makes it possible to limit the friction between the sealing washer 37 and the bottom 6 of the primary flywheel 2. In addition, the sealing washer 37 being pre-stressed axially, it allows to press the sealing washer 19 against the bottom 6 of the primary flywheel 2. Thus, the sealing washer 37 exerts on the sealing washer 19 an axial load to move axially when from its movement from its position of installation of the fasteners to its sealing position of the primary flywheel 2.
    The sealing washer 19, illustrated in FIGS. 18 and 19, differs from the closure washer of the embodiment of FIGS. 16 and 17 in that it comprises resilient tongues 39 whose free end 40 is able to come in abutment against an annular flange carried by the primary flywheel 2 so as to press said sealing washer 19 against the bottom 6 of the primary flywheel 2. In the embodiment shown, the elastic tongues 40 extend in substantially tangential directions along the radially inner edge of the sealing washer 19. The number and dimensioning of the elastic tongues 40 are adapted so as to exert sufficient axial load to allow the plugs 25 to engage inside the orifices 18 of the steering wheel primary 2 during the movement of the sealing washer 19 between its position of installation of the fasteners and its sealing position of the steering wheel p 2. Such resilient tongues 39 are capable of acting as a replacement for or in addition to the spring washer 20 of the embodiments of FIGS. 1 to 15 or the sealing washer 37 of FIG. 16.
    In the embodiment illustrated in FIG. 20, the sealing washer 19 is disposed against the rear face of the bottom 6 of the primary flywheel 2. The sealing washer 19 is held against the bottom 6 of the primary flywheel by means of a support washer 41. The support washer 41 is made of sheet metal, and is fixed by riveting on the bottom 6 of the primary flywheel 4. The support washer 41 comprises an outer zone 42 pressed against the bottom 6 of the primary flywheel 2 and a internal zone 50 forming a flange which, with the bottom 6 of the primary flywheel 2, sandwiches the sealing washer 19.
    As in the previous embodiments, the sealing washer 19 has openings 24 which are arranged vis-à-vis the orifices 18 of the primary flywheel 1 when the sealing washer 19 is in its position of installation of the organs. and the plugs 25 which are engaged in the orifices 18 of the primary flywheel 2 when the sealing washer 19 is in its sealing position of the primary flywheel 2. The axial load pressing the sealing washer 19 against the bottom 6 the primary flywheel 2 is here exerted by the support washer 41. To pass the sealing washer 19 from its installation position of the fasteners to its sealing position of the primary flywheel 2, it is also possible to using a drive tool comprising rods intended to be housed in cavities 32 formed inside the plugs 25.
    In Figures 21 and 22, there is a double damping flywheel according to another embodiment. The web 15 has a plurality of tabs 43 extending radially inwards in which are formed the passage holes of the rivets 17. The tabs 43 are each bordered by two notches 44. The sealing washer 19 comprises a plurality of stop elements 45 which each project axially inside one of the aforementioned indentations 44 when the sealing washer 19 is in its position of installation of the fasteners. As shown in FIG. 21, in this installation position of the fasteners, each abutment element 45 is in contact with two adjacent tabs 43 and thus makes it possible to temporarily immobilize the primary and secondary wheels 2 in a position determined angle. As for the embodiment of FIGS. 1 to 10, when a torque greater than a threshold is transmitted between the primary flywheel 2 and the secondary flywheel 3, a relative rotation between the primary flywheel 2 and the secondary flywheel 3 occurs so that the sealing washer 19 is rotated about the X axis relative to the primary flywheel 2. The sealing washer 19 can thus be moved to its sealing position of the primary flywheel 2. The axial dimension of the stop elements 45 is such that when the sealing washer 19 is in its sealing position, they are no longer in the path of the web 15.
    In relation to FIG. 22, it is also observed that the openings facing the orifices 18 of the primary flywheel are not openings with a closed periphery such as the circular openings of FIGS. 1 to 10 but are formed by indentations 46. formed in the sealing washer 19 on either side of each plug 25.
    Figures 23 and 24 illustrate a double damping flywheel 1 according to another embodiment. In this embodiment, the hub 5 and the bottom 6 of the primary flywheel 2 are monobloc. Therefore, a bearing washer 47 is fixed against the bottom 6 of the primary flywheel 2, for example by riveting, and comprises an annular flange 48 on which the elastic washer 20 bears in order to press the sealing washer 19 against the bottom 6 of the primary flywheel 1. Moreover, the elastic washer 20 of frustoconical shape does not have radial tabs and bears against a central portion 48 of the sealing washer 19. The caps 25 and the openings 49 are as to they are formed in a radially outer portion of the sealing washer 19. Note that the openings 49 are here of semicircular shape and formed in the radially outer edges of the sealing washer 19.
    Although the invention has been described in connection with several particular embodiments, it is obvious that it is not limited thereto and that it comprises all the technical equivalents of the means described and their combinations if they are within the scope of the invention. The use of the verb "to include", "to understand" or "to include" and its conjugated forms does not exclude the presence of other elements or steps other than those set out in a claim. The use of the indefinite article "a" or "an" for an element or a step does not exclude, unless otherwise stated, the presence of a plurality of such elements or steps.
    In the claims, any reference sign in parentheses can not be interpreted as a limitation of the claim.
    权利要求:
    Claims (16)
    [1" id="c-fr-0001]
    1. Double damping flywheel (1) for a motor vehicle comprising: - a primary flywheel (2) and a secondary flywheel (3) movable in rotation relative to each other about an axis X; - a web (15) fixed to the secondary flywheel (3) by fasteners (17) distributed around the axis X; and - resilient members (11) interposed between the primary flywheel (2) and the sail (15) and capable of transmitting torque and damping the rotation acyclisms between the primary flywheel (2) and the secondary flywheel (3); the primary flywheel (2) having a plurality of orifices (18) which are each formed opposite one of said fastening members (17) to allow the installation of said fasteners; said double damping flywheel (1) further comprising a sealing washer (19) which is pressed axially against the primary flywheel (2) and has a plurality of openings (24, 46, 49) distributed around the X axis and a plurality of plugs (25) projecting axially toward the primary flywheel (2) and are each disposed between two adjacent openings (24, 46, 49) of said plurality of openings; said closure washer (19) being adapted to rotate about the X axis relative to the primary flywheel (2) and to move axially relative to the primary flywheel (2) to move from an installation position said fasteners in which the openings (24, 46, 49) are each facing one of said holes (18) of the primary flywheel (2) and the plugs (25) are pressed against the primary flywheel (2) a sealing position of the primary flywheel in which the plugs (25) are each engaged in one of said orifices (18) of the primary flywheel (2).
    [2" id="c-fr-0002]
    2. Double damping flywheel according to claim 1, wherein the sealing washer (19) is axially pressed against a face of the primary flywheel (2) facing the web (15).
    [3" id="c-fr-0003]
    3. Dual damping flywheel according to claim 1 or 2, wherein the sealing washer (19) comprises at least a first abutment surface (26,45) which is arranged such that: - when the sealing washer (19) is in its position of installation of the fasteners, said first abutment surface (26, 45) is adapted to cooperate with a second abutment surface (17, 43) integral in rotation of the web (15), when a relative rotation of the secondary flywheel (3) relative to the primary flywheel (2), so as to move the sealing washer (19) towards its sealing position of the primary flywheel; and that - when the sealing washer (19) is in its position of sealing the primary flywheel, said first abutment surface (26, 45) is not adapted to cooperate with the second abutment surface <17, 43 ), during a relative rotation of the secondary flywheel (3) relative to the primary flywheel (1).
    [4" id="c-fr-0004]
    4. Double damping flywheel according to claim 3, wherein the sealing washer (19) comprises at least two first abutment surfaces (26, 45) and the double damping flywheel (1) comprises at least two second abutment surfaces ( 17, 43) integral in rotation of the web (15); the first two abutment surfaces (26, 45) being respectively arranged to cooperate with one of the two second abutment surfaces (17, 43) during the relative rotation of the secondary flywheel (3) with respect to the primary flywheel (2) in a first direction of rotation and with the other of the two second surfaces during the relative rotation of the secondary flywheel (3) relative to the primary flywheel (2) in a second direction of rotation.
    [5" id="c-fr-0005]
    5. Dual damping flywheel according to claim 4, wherein the first two abutment surfaces (26, 45) and the two second abutment surfaces (17, 43) are adapted to immobilize the secondary flywheel relative to the primary flywheel in a position angular determined when the sealing washer (19) is in its position of installation of fasteners.
    [6" id="c-fr-0006]
    6. Double damping flywheel according to claim 4 or 5, wherein the first abutment surfaces are formed by a flange (26) bordering one of the openings (24) of the sealing washer (19) and projecting axially towards the web (15) in which the second abutment surfaces are formed by the fixing member (17) facing said opening (24) of the sealing washer (19) when the sealing washer (19) ) is in its installation position of the fasteners.
    [7" id="c-fr-0007]
    7. Double damping flywheel according to claim 5 or 6, wherein the fasteners (37) pass through tabs (43) of the web bordered by notches (44) and wherein the sealing washer (19) comprises at least one abutment element (45) protruding axially in one of the indentations (44) when the sealing washer is in its position of installation of the fasteners, the abutment element forming the first abutment surfaces and the tabs (43) bordering said recess (44) forming the second abutment surfaces.
    [8" id="c-fr-0008]
    8. Dual damping flywheel according to claim 2, wherein the sealing washer (19) comprises a cavity (32) formed on one face of the sealing washer (19) directed towards the web (15), said cavity (19) 32) being intended to receive a rod (31) of a drive tool (30) able to move the sealing washer (19) from its position of installation of the fasteners to its position of sealing the steering wheel primary (2) during a relative rotation of the secondary flywheel (3) relative to the primary flywheel (2), the secondary flywheel (3) and the sail (15) being each equipped with an orifice (33, 34) in view of said cavity (32) when the sealing washer (19) is in its installation position, said orifices (33, 34) of the secondary flywheel (3) and the web (15) being adapted to allow the passage of the rod (31) of said drive tool (30).
    [9" id="c-fr-0009]
    9. Double damping flywheel according to any one of claims 1 to 8, further comprising a spring washer (20) which is, on the one hand, in abutment against an annular rim (21) carried by the primary flywheel (21). and, secondly against the sealing washer (19) to press the sealing washer (19) against the primary flywheel (2).
    [10" id="c-fr-0010]
    10. Double damping flywheel according to any one of claims 1 to 9, wherein the spring washer (20) has tabs (22) radially external bearing against the sealing washer (19), said tabs (22) being received in housings (23) formed in the sealing washer (19) so as to fasten in rotation the spring washer (20) and the sealing washer (19).
    [11" id="c-fr-0011]
    11. Double damping flywheel according to any one of claims 1 to 10, wherein the sealing washer (19) comprises a plurality of resilient tongues (39) whose free end (40) bears against an annular flange. (21) provided on the primary flywheel (2) to press the sealing washer (19) against the primary flywheel (2).
    [12" id="c-fr-0012]
    12. Double damping flywheel according to claim 10 or 11, wherein the primary flywheel (2) comprises a bottom (6) and a hub (5), the hub comprising a tubular portion (10) of axial orientation and a radial portion. ( ) extending radially outwardly from the tubular portion (10), said radial portion (7) being fixed against the bottom (6) of the primary flywheel (1) and wherein the sealing washer ( 19) is arranged axially between an annular flange (21) formed in an outer edge of the radial portion (7) of the hub (5) and the bottom (6) of the primary flywheel (1).
    [13" id="c-fr-0013]
    13. Double damping flywheel according to claim 1, wherein the sealing washer (19) is axially pressed against a face of the primary flywheel (2) opposite the web (15).
    [14" id="c-fr-0014]
    14. Double damping flywheel according to any one of claims 1 to 13, wherein the sealing washer (19) comprises a circular bulge (27) projecting towards the primary flywheel (2) and extending around each plugs (25).
    [15" id="c-fr-0015]
    15. Double damping flywheel according to any one of claims 1 to 13, wherein each of the plugs (25) is arranged inside a window (28) formed in the sealing washer (19) and is connected at one edge of the window by a plurality of arms (29).
    [16" id="c-fr-0016]
    16. Double damping flywheel according to any one of claims 1 to 15, wherein the primary flywheel (2) comprises a bottom (6), a cover (9) and a cylindrical portion (8) extending axially between the bottom (6) and the lid (9); the bottom (6), the cover (9) and the cylindrical portion (8) defining an annular chamber, filled with lubricant, in which are housed the elastic members (11); the double damping flywheel (1) further comprising two sealing washers (36, 37) fixed to the web (15) and arranged on either side thereof; the sealing washer (19) having an outer zone (38) sandwiched between one of the sealing washers (37) and the bottom (6) of the primary flywheel (2).
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    同族专利:
    公开号 | 公开日
    FR3039240B1|2017-07-28|
    CN106382333B|2020-06-23|
    DE102016112881A1|2017-01-26|
    CN106382333A|2017-02-08|
    MX2016009482A|2017-09-01|
    KR20170010726A|2017-02-01|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    FR2736116A1|1995-06-27|1997-01-03|Valeo|SHOCK ABSORBER FLYWHEEL INTENDED TO BE INTERPOSED IN A MOTOR VEHICLE DRIVE UNIT COMPRISING IMPROVED SEALING MEANS|
    DE102013205919A1|2013-04-04|2014-10-09|Schaeffler Technologies Gmbh & Co. Kg|torsional vibration dampers|US20190277367A1|2018-03-07|2019-09-12|Vibracoustic Gmbh|Securing and centring device and vibration damping device including same|FR2958704B1|2010-04-09|2012-05-11|Valeo Embrayages|DOUBLE SHOCKWHEEL, IN PARTICULAR FOR MOTOR VEHICLE.|
    KR101406656B1|2012-12-10|2014-06-11|현대자동차주식회사|Dual mass flywheel|
    CN203926595U|2014-05-03|2014-11-05|上海龙创汽车设计有限公司|Double mass flywheel|
    CN204061720U|2014-07-07|2014-12-31|吉林大华机械制造有限公司|A kind of double mass flywheel with waterproof dish pad|FR3065772B1|2017-04-27|2019-04-26|Valeo Embrayages|TORSION DAMPER AND MOTOR VEHICLE|
    KR102005152B1|2017-10-26|2019-07-29|주식회사평화발레오|Dual mass flywheel|
    KR102066348B1|2018-04-30|2020-01-14|주식회사평화발레오|Dual mass flywheel|
    法律状态:
    2016-07-29| PLFP| Fee payment|Year of fee payment: 2 |
    2017-01-27| PLSC| Search report ready|Effective date: 20170127 |
    2017-07-31| PLFP| Fee payment|Year of fee payment: 3 |
    2018-07-27| PLFP| Fee payment|Year of fee payment: 4 |
    2019-07-31| PLFP| Fee payment|Year of fee payment: 5 |
    2020-07-31| PLFP| Fee payment|Year of fee payment: 6 |
    2021-07-29| PLFP| Fee payment|Year of fee payment: 7 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1556836A|FR3039240B1|2015-07-20|2015-07-20|DOUBLE SHOCK ABSORBER WHEEL COMPRISING A SHUTTER WASHER TO ENSURE THE SEALING OF THE PRIMARY WHEEL|FR1556836A| FR3039240B1|2015-07-20|2015-07-20|DOUBLE SHOCK ABSORBER WHEEL COMPRISING A SHUTTER WASHER TO ENSURE THE SEALING OF THE PRIMARY WHEEL|
    DE102016112881.3A| DE102016112881A1|2015-07-20|2016-07-13|A dual-mass damper flywheel comprising a shutter disc adapted to ensure sealing of the primary flywheel|
    MX2016009482A| MX2016009482A|2015-07-20|2016-07-19|Double damping flywheel comprising a sealing washer capable of ensuring sealing of the primary flywheel.|
    KR1020160091318A| KR20170010726A|2015-07-20|2016-07-19|Double damping flywheel comprising a sealing washer capable of ensuring sealing of the primary flywheel|
    CN201610873928.XA| CN106382333B|2015-07-20|2016-07-20|Damper of the twin flywheel type comprising a sealing gasket ensuring the tightness of the primary flywheel|
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