• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a pendulum damping device (1) comprising at least one pendulum mass (3) movably mounted on a support (2) intended to be rotated about an axis, said mass (3) comprising at least two parts located axially on either side of the support (2), at least one spacer (12) connecting the two parts of each mass (3) and passing through an opening (8) of the support (2), an element bearing (11) being located between an edge (9) of the opening (8) and the spacer (12), the spacer (12) and the running member (11) being mounted with a first clearance ( J1) in said opening (8), characterized in that the support (2) comprises first abutment means (31) adapted to cooperate with second abutment means (26) of the mass, so as to limit the radial deflection from the mass (3) to a second game (J2), lower than the first game (J1).
    公开号:FR3018882A1
    申请号:FR1452228
    申请日:2014-03-18
    公开日:2015-09-25
    发明作者:Franck Cailleret；Clement Tondellier；Giovanni Grieco
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    [0001] The present invention relates to a pendular damping device, in particular for a motor vehicle. Such a device, also called pendulum oscillator or pendulum, is particularly intended to equip a transmission of a motor vehicle. In a motor vehicle transmission, at least one torsion damping system is generally associated with a clutch capable of selectively connecting the engine to the gearbox. An internal combustion engine generates acyclisms because of the successive explosions in the cylinders of the engine, these acyclisms varying in particular as a function of the number of cylinders. The damping system conventionally comprises springs and friction elements having the function of filtering the vibrations due to motor rotation acyclisms and intervenes before transmission of the engine torque to the gearbox. This prevents such vibrations pass into the gearbox and cause shock, noise and unwanted noise. In order to further improve the filtration, it is known to use a pendulum damping device in addition to the usual damping system. The patent application FR 2 981 714, in the name of the Applicant, discloses a pendular damping device comprising an annular support intended to be rotated about its axis and pendular masses mounted at the outer periphery of the support. Each mass is driven in a pendulum movement in operation and comprises two parts, mounted axially on either side of the support and connected by three spacers each through an opening of the support. A roller is mounted between a raceway formed in each spacer and the edge of the corresponding opening 30 of the support. The spacers are mounted with a large radial clearance in the openings of the support. In addition, the spacers are fixed to both parts of the mass by riveting. The heads of the rivets are supported on the outer radial faces of the parts of the mass, that is to say on the opposite sides to the annular support. The spacers and the rollers are all located in the same radial plane.
    [0002] In response to rotational irregularities or acyclisms, each mass moves in such a way that its center of gravity oscillates in a pendulum fashion. The oscillation frequency of each mass is proportional to the rotational speed of the motor shaft, the corresponding multiple may for example take a value close to the rank of the overriding harmonic of the vibrations responsible for the high irregularities of rotation in the vicinity of the idle . In operation, during the rotation of the support, the pendular masses are subjected to the centrifugal effect. Conversely, when stopping the vehicle or when the engine is running at low speed, the masses can fall back under the effect of their own weight, depending on their position. During this fall of the masses, the spacers fall on the edge of the openings of the support, which can generate noise. Moreover, there is a risk that the rollers escape from the recesses formed between the spacers and the corresponding edges of the spacers, these rollers then becoming jammed in another area of the opening. This then prevents the pendulum masses from moving normally, which affects the operation of the pendulum damping device. The invention aims in particular to provide a simple, effective and economical solution to these problems.
    [0003] For this purpose, it proposes a pendulum damping device comprising at least one pendular mass movably mounted on a support intended to be rotated about an axis, said mass comprising at least two parts located axially on both sides. other of the support, at least one spacer which connects the two parts of each mass and passes through an opening of the support, a running member located between an edge of the opening and the spacer, the spacer and the rolling member being mounted with a first clearance in said opening, characterized in that the support comprises first abutment means 5 adapted to cooperate with second stop means of the mass, so as to limit the radial movement of the mass to a second set In this way, the aforementioned abutment means limit the radial displacement of the mass relative to the support, and thus the height of fall of the corresponding mass. e. Noise is thus reduced during the stopping of the engine of the vehicle, when the masses are no longer centrifuged, or at low engine speed, when the centrifugal effect is no longer sufficient to compensate for the weight of each mass. Moreover, in the case where the spacers are equipped with damping means formed for example by an elastomeric strip, the first and second abutment means make it possible to avoid or limit crushing and premature damage to these means. amortization. Preferably, the second clearance is between 0.3 and 1 mm. According to one embodiment of the invention, the first stop means comprise at least one protruding member, the second abutment means being formed by the edge of a cutout formed in at least one part of the mass. . In this case, the cutout may be formed and may lead to the radially inner edge of the corresponding part of the mass, the cutout delimiting a generally M-shaped edge on which the protruding member is intended to come into contact with. in order to limit the radial movement of the mass relative to the support. The generally M-shaped edge has a convex median central portion 30, on either side of which two concave end zones are formed.
    [0004] The concave end zones then form two abutment zones capable of cooperating with the protruding member so as to limit the angular displacement of the masses relative to the support, around the axis of rotation of the support. This limitation of the angular deflection, combined with the limitation of the radial displacement, makes it possible to prevent the rolling elements from escaping from their housings situated between the spacers and the edges of the corresponding cuts. This ensures the smooth operation of the damping device. The generally shaped edge of M may be symmetrical with respect to a radial plane. Alternatively, this edge may have an asymmetrical shape. For example, the concave end zone situated upstream with respect to the direction of rotation of the support may comprise two lateral abutment surfaces, able to maintain, at least during a period of operation, the protruding member in the zone d concave end upstream. In this case, the projecting member may be cylindrical, the upstream concave end zone having a downstream lateral abutment surface forming an angle less than or equal to 60 ° with respect to the radial direction. In a preferred example, the angle is less than or equal to 200. In a variant, the cutout is formed and opens out on the radially inner edge of the corresponding part of the mass, the cut comprising a succession of concave recesses in which the protruding member is intended to come into abutment so as to limit the deflection Radial of the mass relative to the support. According to another embodiment, the second stop means comprise a projecting member, the first abutment means being formed by the edge of a cutout formed in the support. In this case, the cutout formed in the support is formed and opens out on the radially outer edge of the support.
    [0005] The protruding member may have a circular or triangular section. Moreover, it can be made of metal or synthetic material. Advantageously, the opening of the support, the spacer, and the first and second abutment means are made so that the second clearance is substantially constant over the entire angular range of movement of the mass relative to the support. This ensures that regardless of the angular position of the mass relative to the support, the mass drop is relatively low. The invention will be better understood and other details, characteristics and advantages of the invention will become apparent on reading the following description given by way of non-limiting example with reference to the accompanying drawings, in which: FIGS. 1 and 2 are perspective views of a portion of a pendulum damping device according to a first embodiment of the invention, in two different angular positions of the mass relative to the support, - Figures 3 and 4 are views. of faces of a part of the device, in the positions illustrated respectively in Figures 1 and 2, - Figures 5 and 6 are radial sections of a part of the device, respectively when the masses are subjected to a centrifugal effect and when the masses have little or no such centrifugal effect; FIG. 7 is a front view of part of a pendulum damping device, according to a second embodiment of FIG. FIG. 8 is a perspective view of a portion of a pendulum damping device according to a third embodiment of the invention, FIGS. 9, 11, 12 and 13 are front views. a portion of a pendulum damping device, according to a fourth embodiment of the invention, in several successive angular positions of the support, Figure 10 is a detail view of Figure 9, illustrating in particular the shape 14 and 15 are front views of a portion of a pendulum damping device, according to a fifth embodiment of the invention, FIG. 16 is a front view of a portion of a of a pendular damping device according to a sixth embodiment of the invention. Figures 1 to 6 show a damping device 1 for a motor vehicle according to a first embodiment of the invention. That comprises an annular support 2, such as for example an annular web of a double damping flywheel or a phasing washer of a LTD type damper (Long Travel Displacement). Masses 3 are movably mounted on the support 2. More particularly, the annular support 2 comprises an inner annular portion 4, connected to an outer annular portion 5 by radially extending tabs 6. The plane of the inner annular portion 4 is offset axially from that of the outer annular portion 5. Each radial lug 6 has three holes 7 for the passage of fastening rivets. Furthermore, the outer annular portion 5 of the support 2 comprises six pairs of openings 8. Each opening 8 has a general shape of isosceles triangle whose vertices 9 are rounded and whose base 10 is located radially inside. The opposite vertex 9 to the base 10 is curved and forms a raceway intended to cooperate with a roller 11. Six masses 3 are mounted on the outer annular portion 5 of the support 2. Each mass 3 comprises a first portion 3a and a second part 3b, arranged axially on either side of the support 2, facing one another. The two parts 3a, 3b are interconnected by two spacers 12. Each part 3a, 3b of the mass 3 comprises a so-called internal radial face, turned towards the support 2, and an external radial face, opposite to the internal radial face. . In addition, each portion 3a, 3b has an arcuate shape and has a radially inner peripheral edge 13 and a radially outer circumferential edge 14 curves, connected by radial lateral edges 15. Each portion has two openings 16, intended for mounting by force-fitting spacers 12. Each opening 16 has an oblong shape and has a radially inner edge 17 generally straight, a radially outer edge 18 arc-shaped, connected by two rectilinear side edges 19 (Figure 1). The connection areas between the lateral edges 19 on the one hand, and the radially inner and outer edges 17, 18, on the other hand, are rounded. The radially outer edge 18 has a rounded recess 20 in the middle part. Each spacer 12 has a generally constant section along its entire length. More particularly, each spacer 12 has an inner peripheral edge 21 and an outer peripheral edge 22 curves (Figures 1 and 3). The outer peripheral edge 22 is concave and forms a raceway for the corresponding roller 11. The inner peripheral edge 21, of convex shape, has two rounded recesses 23 at its circumferential ends. Thus, in front view, each spacer 12 has two rounded lateral horns 24 at its outer peripheral edge 22, which is housed in the two radially outer connection areas of the corresponding openings 16. The rounded shapes of the horns 24 and said connecting zones are generally complementary. A damping element 25 in the form of an elastomeric strip may be fixed on each spacer 12, for example by gluing, between the parts 3a, 3b of each mass 3. This damping element 25 extends from one horn 24 to the other, along the inner peripheral edge 21. A radial clearance J1 is formed between the inner peripheral edge of each spacer (or each damping element when it is present) and the base 17 of the corresponding opening 16, when the masses 3 are subjected to a centrifugal effect in operation, that is to say when the rollers 11 are in contact both with the spacers 12 and the apices 9 of the openings 8. According to FIG. the invention, the radially inner edge 13 of each of the parts 3a, 3b of the masses 3 comprises a cutout 26 located in a median zone of said edge 13. The cutout 26 opens out at this edge 13 and has a general shape of M, symmetrical with respect to the pla n radial median 27 of the mass 3. This cutout 26 delimits a radially inwardly directed edge, comprising a convex median central portion 28 in an arc of a circle, on either side of which are formed two concave end zones 29 Each end region 29, 30 has a generally circular arc shape and is intended to form a stop. By way of example, the radius of curvature of the median portion 28 is between 10 and 30 mm, the radius of curvature of the end zones 29, 30 is between 2 and 5 mm.
    [0006] For each mass 3, the support 2 further comprises a pin or a cylindrical pin 31 extending axially from only one of the radial faces of the radially outer portion 5 of the support 2, said pin 31 being located opposite the blank corresponding. The diameter of the pin 31 is for example between 4 and 6 mm.
    [0007] In operation, when the masses 3 are subjected to the centrifugal effect, a radial clearance J2 is formed between the edge of the cutout 26 and the cylindrical pin 31. This game J2 is for example of the order of a quarter of the game J1. It is for example between 0.3 and 1 mm. The shape of the raceways 9, 22 and the shape of the cuts 26 30 are adapted so that the clearance J2 is generally constant, regardless of the positions of the pendular masses 3 relative to the support 2. In operation, the edge the cut 26 and the cylindrical pin 31 are intended to form complementary stops.
    [0008] In particular, as can be seen in FIGS. 2 and 4, the pin is intended to be housed, at least in part, in the concave end zones 29, 30, so as to limit the displacement of the corresponding mass 3 by relative to the support 2 This makes it possible in particular to prevent the rollers 11 from escaping from the recesses formed between the corresponding raceways 9, 22, so as to guarantee the proper operation of the pendulum masses 3. Moreover, during the stopping the vehicle engine, that is to say when the rotation of the support 2 is stopped, the masses 3 are no longer subjected to the centrifugal effect. Some of these masses 3 can then fall back under the effect of their own weight. This drop is relatively low and is limited to the value of the game J2, which reduces noise or noise perceived by the passenger of the vehicle. This phenomenon can also occur at low engine speeds. Furthermore, when the engine is stopped or when it runs at low speed, the mass 3 which rests on the pin 31 tends to tilt relative to the support 2, that is to say to pivot relative to an axis perpendicular to the axis of rotation of the support 2, as shown in Figure 6. The inner faces of the parts 3a, 3b of the mass then bear and rub against the radial faces of the outer portion 5 of the support 2, which has the effect of curbing the fall of the mass 3 and limit the noise due to this fall. FIG. 7 illustrates a second embodiment of the invention, which differs from that previously described in that the cutout 26 comprises a succession of concave recesses 29, 30, 32 in the shape of an arc of a circle, in which the counter 31 is intended to bear in order to limit the movement of the mass 3 relative to the support 2.
    [0009] The various recesses 29, 30, 32 allow each to maintain in position, to a certain extent, the mass 3 relative to the support 2 when the engine is stopped or runs at low speed, by inserting the pin 31 into one of the recesses 29, 30, 32. The radius of curvature of each recess 29, 30, 32 corresponds substantially to half the diameter of the pin 31. FIG. 8 illustrates a third embodiment of the invention, in which each portion 3a, 3b masses 3 comprises a cutout 26 in the form of a circular arc in a radially median zone of said portion 3a. The pin 31 extends axially in the cutout 26 of only one of the two parts 3a, 3b. The width L of the cutout 26, that is to say its dimension perpendicular to the longitudinal edges of the cut, is equal to at least the diameter of the peg 21 plus the value of a set J2. In this way, in case of stopping the rotation of the support 2 for example, the fall of the masses 3 falling under the effect of their own weight is stopped by pressing the pin 21 on the radially outer edge 33 of the cutout 26. As previously, the pin 31 can also come to bear on the rounded ends 34 of the cutout 26, so as to prevent the rollers 11 from leaving the corresponding rolling tracks 9, 22.
    [0010] Alternatively (not illsutrée), another pin such as 31 may be provided arranged opposite each of the ends 3a, 3b. In total, three pins such as 31 would extend axially each through a cutout such as 26. FIGS. 9 to 14 illustrate a fourth embodiment of the invention, which differs from that described with reference to FIGS. 6 in that the cutout 26 is asymmetrical. In particular, as illustrated in FIG. 10, the concave end zone 29 situated upstream with respect to the direction of rotation of the support (indicated by the arrow 35) has two lateral abutment surfaces 36, 37, able to hold in position at least during a period of operation, the pin 31 in the upstream concave end zone 29.
    [0011] The upstream concave end zone 29 further comprises a substantially rectilinear bottom surface 38 extending between the two lateral abutment surfaces 36, 37. The upstream lateral abutment surface 36 has a circular arc shape, the radius of curvature is between 2 and 5mm, and whose tangent at the radially outer point has an angle α between 25 and 600. The downstream lateral abutment surface 37 extends in a plane forming an angle a2 between 10 and 20 ° relative to the radial plane, this surface being connected to the bottom surface 38 by a rounded area 39 in an arc whose radius of curvature is between 2 and 5mm, for example. The downstream portion of the upstream end zone 29 is deeper than its upstream portion. This means that the downstream end 40 of the bottom surface 38 is further from the circumference of the radially inner edge 13 of the mass 3 than the upstream end 41 of the bottom surface 38. More particularly, the radial distance h between the end 40 of the bottom surface 38 and the circumference of the inner edge 13 is for example between 2 and 5mm, and is preferably greater than half the diameter of the pin 31, between 4 and 6 mm. The convex median zone 28 extends over an angular range between 0 and 30 °, for example. The downstream concave end zone 30 has a geometry similar to that described with reference to FIGS. 1 to 4. In operation, when the masses 3 do not undergo a sufficient centrifugal force (low speed of rotation of the motor and the support 2, by example), these can be held in position by insertion of the pin 31 in the downstream concave end zone 30 (due to the fall of the masses 3), when the masses 3 are located in the upper part of the support 2 (c). that is to say above the median horizontal plane passing through the axis of rotation of the support 2), as illustrated in FIGS. 11 and 14. In the positions represented in these figures, the pin 31 comes to bear against the one or other of the abutment surfaces 36, 37.
    [0012] Conversely, when the mass 3 is located in the lower part of the support 2, that is to say below the median horizontal plane passing through the axis of rotation of the support 2), as illustrated in FIGS. and 13, the mass 3 falls down under the effect of its weight (illustrated by the vector Fg) and the pin 31 is extracted from the cutout 26. FIGS. 15 and 16 illustrate a fifth embodiment of the invention , wherein each portion 3a, 3b of each mass 3 comprises a stud 42 extending axially towards the opposite portion 3b, 3a, said stud 42 having a generally triangular. More particularly, the stud 42 has a base 43 rotated radially outwardly and a rounded apex 44 rotated radially inwards. The stud 43 is intended to cooperate with the edge of a cutout 45 formed at the radially outer edge 46 of the outer portion 5 of the support 2. The cutout 45 has a W shape and comprises two oblique lateral surfaces 48 with respect to the radial direction, each forming an angle between 30 and 600 relative to the radial plane. The cutout 45 further delimits in the support 2 a triangular central zone 46 whose apex 47 is turned radially outwards. This vertex 47 is set back radially inward with respect to the circumference of the outer edge 46 of the support 2. The cutout 45 defines two recesses, each of complementary shape to that of the triangular pad 42. As before, this complementarity of shape makes it possible to maintain the mass 3 in position at low rotational speeds of the motor and the support 2, and for masses 3 situated at the upper part of the support 2. FIG. 17 illustrates a sixth embodiment of the invention, which differs from that shown in Figures 15 and 16 in that the triangular pad 43 is replaced by a pin or a cylindrical pin 49. The operation of such a device 1 remains unchanged.
    权利要求:
    Claims (14)
    [0001]
    REVENDICATIONS1. Pendulum damping device (1) comprising at least one pendulum mass (3) movably mounted on a support (2) intended to be rotated about an axis, said mass (3) comprising at least two parts ( 3a, 3b) located axially on either side of the support (2), at least one spacer (12) which connects the two parts (3a, 3b) of each mass (3) and passes through an opening (8) of the support (2), a rolling member (11) located between an edge (9) of the opening (8) and the spacer (12), the spacer (12) and the rolling member (11) being mounted with a first play (J1) in said opening (8), characterized in that the support (2) comprises first abutment means (31) adapted to cooperate with second abutment means (26) of the mass, so as to limit the radial displacement of the mass (3) to a second game (J2), lower than the first game (J1).
    [0002]
    2. Device (1) according to claim 1, characterized in that the second set (J2) is between 0.3 and 1 mm. 20
    [0003]
    3. Device (1) according to claim 1 or 2, characterized in that the first abutment means comprise at least one projecting member (31), the second abutment means being formed by the edge (28, 29, 30). a cutout (26) formed in at least one of the portions (3a, 3b) of the mass (3). 25
    [0004]
    4. Device (1) according to claim 3, characterized in that the cutout (26) is formed and opens on the radially inner edge (13) of the corresponding portion (3a) of the mass (3), the cut (26) ) delimiting an edge (28, 29, 30) in the general shape of M on which the projecting member (31) is intended to come into abutment so as to limit the radial displacement of the mass (3) relative to the support (2).
    [0005]
    5. Device (1) according to claim 4, characterized in that the edge (28, 29, 30) in the general shape of M comprises a convex median central portion (28), on either side of which two concave end zones (29, 30) are formed.
    [0006]
    6. Device (1) according to claim 5, characterized in that the edge (28, 29, 30) in the general shape of M is symmetrical with respect to a radial plane (27).
    [0007]
    7. Device (1) according to claim 5, characterized in that the concave end zone (29) located upstream relative to the direction of rotation (35) of the support comprises two lateral abutment surfaces (36, 37), adapted to maintain, at least during a period of operation, the protruding member (31) in the upstream concave end zone (29).
    [0008]
    8. Device (1) according to claim 7, characterized in that the protruding member (31) is cylindrical, the upstream concave end zone (29) having a downstream lateral abutment surface (37) forming an angle ( a2) less than or equal to 20 ° with respect to the radial direction.
    [0009]
    9. Device (1) according to one of claims 1 to 4, characterized in that the cutout (26) is formed and opens on the radially inner edge (13) of the corresponding portion (3a) of the mass (3). ), the cutout (26) comprising a succession of concave recesses (32) in which the projecting member (31) is intended to come into abutment so as to limit the radial movement of the mass (3) relative to the support (2).
    [0010]
    10. Device (1) according to claim 1 or 2, characterized in that the second abutment means comprise a projecting member (42, 49), the first abutment means being formed by the edge of a cutout (45). arranged in the support (2).
    [0011]
    11. Device (1) according to claim 10, characterized in that the cutout (45) formed in the support (2) is formed and opens on the radially outer edge (46) of the support (2).
    [0012]
    12.Dispositif (1) according to claim 10 or 11, characterized in that the protruding member (42, 49) has a circular or triangular section.
    [0013]
    13. Device (1) according to one of claims 1 to 12, characterized in that the opening (8) of the support (2), the spacer (12), and the first and second abutment means are made of so that the second clearance (J2) is substantially constant over the entire angular range of movement of the mass (3) relative to the support (2).
    [0014]
    14. Device (1) according to one of claims 1 to 13, characterized in that the protruding member (31) extends from one side only of the support (2).
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    同族专利:
    公开号 | 公开日
    FR3018882B1|2018-03-02|
    DE102015103529A1|2015-10-29|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US2348941A|1942-12-05|1944-05-16|Packard Motor Car Co|Vibration damping device|
    DE102006028556A1|2005-07-11|2007-01-18|Luk Lamellen Und Kupplungsbau Beteiligungs Kg|Torque transmission device for torque transmission between drive unit e.g. internal combustion engine has castors which consists of collar, arranged between pendulum mass and pendulum mass supporting unit|
    US20130098198A1|2011-10-20|2013-04-25|Chrysler Group Llc|Pendulum vibration absorber on a crankshaft|
    WO2013156733A1|2012-04-20|2013-10-24|Valeo Embrayages|Pendular damping device, especially for a motor vehicle transmission|US20160153521A1|2014-11-28|2016-06-02|Valeo Embrayages|Device for damping torsional oscillations|
    EP3163118A1|2015-11-02|2017-05-03|Valeo Embrayages|Device for damping torsional oscillations|
    FR3047784A1|2016-02-17|2017-08-18|Valeo Embrayages|PENDULAR DAMPING DEVICE|
    FR3047785A1|2016-02-17|2017-08-18|Valeo Embrayages|PENDULAR DAMPING DEVICE|
    FR3048271A1|2016-02-26|2017-09-01|Valeo Embrayages|PENDULAR DAMPING DEVICE|
    WO2018033170A1|2016-08-15|2018-02-22|Schaeffler Technologies AG & Co. KG|Centrifugal pendulum|FR2981714B1|2011-10-19|2013-11-01|Valeo Embrayages|PENDULUM OSCILLATOR TYPE DAMPING SYSTEM WITH IMPROVED GUIDE DEVICE|
    法律状态:
    2016-03-31| PLFP| Fee payment|Year of fee payment: 3 |
    2017-03-31| PLFP| Fee payment|Year of fee payment: 4 |
    2018-03-29| PLFP| Fee payment|Year of fee payment: 5 |
    2020-03-31| PLFP| Fee payment|Year of fee payment: 7 |
    2021-03-30| PLFP| Fee payment|Year of fee payment: 8 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1452228|2014-03-18|
    FR1452228A|FR3018882B1|2014-03-18|2014-03-18|PENDULAR DAMPING DEVICE, IN PARTICULAR FOR A MOTOR VEHICLE|FR1452228A| FR3018882B1|2014-03-18|2014-03-18|PENDULAR DAMPING DEVICE, IN PARTICULAR FOR A MOTOR VEHICLE|
    DE102015103529.4A| DE102015103529A1|2014-03-18|2015-03-11|Pendulum damping device, in particular for a motor vehicle|
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