• 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 the automotive industry and can be used for friction clutches in automobiles. The purpose of the invention is to reduce noise in the work and increase durability. The shock absorber contains two coaxially arranged parts mounted with the possibility of angular displacement relative to each other. The first part includes "1 A hitch claim that is in engagement with the hub when rotating in one direction and freely mounted relative to the hub when rotating in the opposite direction. There are two contrades connected to the disc of the hub, which are also engaged with the hub when rotating in the same direction. The position of the engagement of the hub disc corresponds to the free position of the counter-disks, and vice versa. The second part coaxially includes two guide washers. The angular displacement of coaxially arranged parts occurs after they overcome the action of elastic elements. 4 Cp. F.-ly, 10 Il. / i ate with
    公开号:SU1600642A3
    申请号:SU853947173
    申请日:1985-08-02
    公开日:1990-10-15
    发明作者:Кармилле Роже；Гратон Мишель；Башер Мишель
    申请人:Валео (Фирма)；
    IPC主号:
    专利说明:

    The invention relates to the automotive industry and can be used for (friction clutch in automobiles.
    The purpose of the invention is to reduce noise during operation and increase durability.
    On (lig. 1 the torsional vibration absorber is shown, front view, in Fig. 2 - section A-A in Fig. 15 in Fig. 3 - section B-B in Fig. 2; in FIG. 4 - a hub disk, view Figure 5 shows the hub counterdisk, viewed from the front, Fig. 6, section BB, Fig. 3, Fig. 7 and 9, the first phase of the shock absorber operation, compression of the springs 26, Fig. 8 and 10 - second phase of operation, compression of the springs 27.
    The shock absorber contains two coaxially arranged parts 1 and 2 installed with the possibility of angular displacement relative to each other. Part 1 has a hub 3 for rigid connection with a driven shaft (for example, with the input shaft of a car's gearbox) by means of slots made on the surface of the aperture of the hub 3, and a hub disk 5 connected to the hub 3 with one-way engagement. At least one counterdisk 6, also associated with the hub, is connected to the disk 5 of the hub, and the direction of engagement of the disk 5 of the hub is opposite to the direction of engagement of the counterdisk 6.
    O5
    35

    WITH
    The shock absorber can have two identical counterdiscs 6 located on the opposite hub of the disk 5 hub. In the hub disk 5 there is a central axial hole 7 for mounting the disc on step 3, the counters also have corresponding hairs 8. The disk 5 of the hub provides means for the engagement of the teeth 9, which are made in the form of at least one radial tooth 10 on the outer surface of the hub 3 AND the counter groove,. 11 on the surface of jiocTH hole 7 of the disk 5 of the hub, where the tooth is located in a groove with a lock in the circumferential direction. Identical means 12 zafegshen pr.edu viewed and between the hub 3 and each
    the drive shaft moment is greater than the torque of the driven shaft, since the engine drives the car, means 12 of the engagement between the hub 3 and each of the hub 6 discs are in contact, the grooves 14 and 16 of each of the hub 6 discs abut against the teeth 10 and 13 of the hub 3 its edge, which is rearward relative to the direction of rotation of the node.
    Let J (the circular gap between the teeth 10 and 13 of the hub 3 and the opposite edge of the grooves 14 and 16 of each of the rear disc 6 of the hub (Fig. 5} .. In this case, the means 9 of the engagement between the hub 3 and the hub disk 5 are in contact with opposite
    counterdisc 6. There is a 20 ohm direction tooth on the hub.
    13, and on the surface of the counterdiscs there is a corresponding groove 14, Teeth 10 and 13 are located diametrically opposite to each other. To provide clearance in the circumferential direction, 25, the teeth in the grooves should be fitted with a groove 14 with an additional section mating with section 15 of a hub disk 5, and a groove 11 of a disk disk with an additional 0 section of a counterdisc 6, Grooves 11, 15 and 14, 16 have the same configuration and dimensions D4 and are located: diametrically opposite to each other. Thus, the engaging means 9 between the quenching 3 and the disc of the hub 5 include not only the tooth 10, made on the hub 3, but also the tooth 13, interacting respectively; with the grooves 11, 15 of the disc, st / pice 5. DO Means 12 are meshing between The hub 3 and each of the counter-disks 6 contain not only the tooth 13 made on the hub 3, but also the tooth 10, interacting respectively with the keys 14 and 16 of the counter-disk 6.
    In the neutral position of the node (teril-S), the means 9 of engagement between the hub 3 and the disk 5 of the hub
    In the neutral position of the node, the disk 5 of the hub rests on the teeth of the m 10 and 13 of the hub 3 with the edge of its grooves 11 and 15, which is rearward relative to the direction opposite to the direction of FI.
    Thus, there is a gap J, equal to the previous one, between these teeth 10 and 13 of the hub 3 and the edge of the grooves 1 and 15 of the disk 5 of the hub, which is anterior to this direction of rotation.
    This direction of rotation is opposite to the direction of rotation F and corresponds to the operation of the assembly in compression mode when the torque of the drive shaft becomes less than the torque of the driven shaft.
    In the direction of rotation F, each of the counterdisks 6 of the hub is rigidly connected to the hub 3, while the disk 5 of the hub is free to rotate relative to the hub 3, and vice versa, in the opposite direction of rotation, the disk 5 of the hub is rigidly connected to the hub 3, while each of the counterdisks 6 of the hub is free to rotate relative to the hub 3.
    Therefore, such an alternating selection is made in contact in one direction - Q with the location of the disk 5 of the hub and the rotation of the rotation, and the means 12 of engagement with the gap between the step 3 and each of the counter disks 6 are in contact in the opposite direction of rotation. 55
    With the direction of rotation F, corresponding to the movement of the car, it is foremost and, hence, the operation of the node in the expansion mode, when
    smoke from duplicate counterdiscs
    6 stepping on the most-. pizza 3.
    Thus, the disk 5 of the hub and, the counterdisc 6 of the hub have the same conbziguration, including holes
    7 and 8. And grooves P, 15, 14 and 16, each of the counter disks 6 of the hub, can be obtained from the disk 5 stu In the neutral position of the node the disk 5 of the hub abuts against the teeth of m 10 and 13 of the hub 3 with the edge of its grooves 11 and 15, rearward with respect to the direction opposite to direction FI.
    Thus, there is a gap J, equal to the previous one, between these teeth 10 and 13 of the hub 3 and the edge of the canal 1 and 15 of the disk 5 of the hub, which is front with respect to this direction of rotation.
    This direction of rotation is opposite to the direction of rotation F and corresponds to the operation of the assembly in compression mode when the torque of the drive shaft becomes less than the torque of the driven shaft.
    In the direction of rotation F, each of the counterdisks 6 of the hub is rigidly connected to the hub 3, while the disk 5 of the hub is free to rotate relative to the hub 3, and vice versa, in the opposite direction of rotation, the disk 5 of the hub is rigidly connected to the hub 3, while each of the counterdisks 6 of the hub is free to rotate relative to the hub 3.
    Therefore, such an alternating arrangement of the disk 5 of the hub and each
    smoke from duplicate counterdiscs
    6 stepping on the most-. pizza 3.
    Thus, the disk 5 of the hub and, the counterdisc 6 of the hub have the same conbziguration, including holes
    7 and 8. And grooves P, 15, 14 and 16, each of the counter-disks 6 of the hub, can be obtained from the disk 5 of the hub by rotating it 180 around the diameter T of the entire assembly that passes through the teeth 10 and 13 of the hub 3.
    In the present embodiment, the teeth 10 and 13. are made in the axial direction of the Institute only in the middle part of the hub 3.
    Part 2 contains at least one disk 17 — a guide washer, about an expansion ring around part 3, but free when rotating relative to the hub 3, regardless of the direction of rotation.
    In practice, there are two guide pins 17 located along this and on the other side of the disk 5 of the hub and counterdisk 6 of the hub and rigidly interconnected with the help of axial links 18 passing through the gaps through the holes 19 and 20, provided for this on the outer periphery of the disk 5 of the hub and of the counterdisc 6 of the hub, respectively.
    In the illustrated embodiment, four axial ligaments 18 are provided, arranged X-shaped with respect to the axis of the assembly.
    In accordance with the invention, each of the openings 19 and 20 may, in one of its edges, be in contact with the axial connection 18 passing through it.
    In the neutral position of the node in contact with the corresponding axial ligament 18, that edge of the orifice 19 is frontal with respect to the direction of rotation Fj and the counterdisk 6 is in contact with the corresponding axial ligament 18 with that edge of the orifice 20 that is rearward with respect to the direction rotation F.
    Thus, for a given mechanical strength for the disk 5 and disk 2, the holes 19 and 20 can have maximum dimensions.
    The holes made in each disk or counterdisc have the dimensions necessary to provide an angular deviation between parts 1 and 2, corresponding to working only in the expansion mode or only in the mode of compression of the assembly, instead of having dimensions corresponding to the operation as in the mode expansion, and in compression mode.
    Let JB be the gap present in the neural position of the node between each axial link 18 and that edge of the hole.


    steps 19 and 20, which is located at a distance from this link.
    Part 2 also contains a friction disk 21. Its peripheral part 22, which can be divided into sectors, is glued onto the inner surface of one of the guide washers 17 and is rigidly connected to this guide washer 17 by means of axial links 18, already connected to Insert this guide washer 17 with the second guide plate.
    On the peripheral part 22 of this Friction disk 21, axially protruding friction lining 23 is reinforced on both sides.
    As a result of clamping these friction linings 23 between the two disks, the pressure disk and the supporting disk of the clutch mechanism (not shown), part 2 is rigidly connected to the shaft during rotation.
    In practice, this is a leading shaft.
    In this case, the friction clutch of the car we are talking about the output shaft of the engine car.
    To center part 2 relative to part I between one of the guide washers I7 of part 2 and the hub of part 3, 1 the bearing 24 is radially mounted.
    In practice, this bearing 24 is associated with that of the guide washers 17, on which the peripheral part of the friction disk 21 is glued.
    This bearing 24 is provided with a flange 25, radially protruding perpendicular to the axis of the assembly and located between the corresponding guide washer 17 and the coit disk 6 closest to it.
    The guide washers 17 are located in the axial direction outside the teeth 10 and 13, the hub 3.
    Circular elastic means installed between parts 1 and 2 contain several elastic elements mounted around the axis of the node and tangent to the same circumference of this node.
    In the present embodiment, there are two elastic elements 26 having a relatively weak stiffness, and two elastic elements 27 having a much greater rigidity. These four elastic elements are located crosswise.
    ten
    15
    20
    25
    In practice, these are helical springs. .
    Each of these elastic members 26 and 27 partially enters the holes 28-31 made in the hub disk 5 and in the hub counter-disks 6, and partially enters the holes 32 and 33 made in the guide washers 17.
    On the radially outer, relative to the axis of the assembly, the openings 32 and 33, made in the guide washers 17, are provided with a protruding lip serving to hold the corresponding elastic element 26 and 27.
    At least one, and on the right: - in a tick, both holes 28 and 30, made in the hub disk 5 and counter disks 6 of the hub for relatively elastic stiffness elements 26, have the same circumferential configuration C, corresponding to the circumference of the holes 32 and 33 made in the direction of the puck 17.
    At least one, and in practice, both holes 29 and 31, made in the disk 5 and the countershaft 6 hub for zo elastic elements. 27 of high rigidity, have a size around the circumference of C, which exceeds the size of the circumference of the C 4 4 holes 33 in the guide washers 17, resulting in the neutral position of the node and in at least one direction of rotation these elastic elements 27 are inserted into the holes 29 and 31 in . disk 5 hub and counter, tsiska 6 b annular gap J. This gap Jg is the same for disk 5 of hub and for counterdisk 6, but for disk 5 of hub it is regulated relative to elastic elements 27 S in the opposite direction of FI, and for counterdisk 6 of hub it is regulated relative to the elastic elements 27 in the direction F | ,
    Thus, the holes 29 and 30 have the same circumferential length. Between parts 1 and 2, forming a shock absorber torsional oscillations. - Research institutes, Friction means of known construction work.
    In the present embodiment, these means contain, in addition to the bearing 24, which is rigidly connected, when rotating, with the guide washer 17, two Friks 16006428
    washers 34 located on both sides of the disk 5 of the hub between this disk and each of the counterdisk 6 of the hub.
    An elastic washer 35, such as a cup spring, which compresses the entire assembly in the axial direction, is installed between the guide washer 17, opposite the one with which the Friction disk 34 is connected, and the rear disk 6 of the hub closest to this guide washer 17.
    In practice, a clamping washer 36 is connected between the elastic washer 35 and the corresponding counterdisc 6 of the hub, which, when rotating, is connected to the guide washer 17 by means of la-pok 37.
    In the course of operation, when the car is moving forward, the torque is applied to part 2 and, consequently, to guide washers 17 belonging to this part, rotating in direction P |, these guide washers through circular means 26 and 27 t in the rotation part 1 and, therefore, the hub 3.
    When working in the extension mode, i.e. in the mode when the torque of the drive shaft is greater than the rotational moment of the driven shaft, it is the hub 3 that rotates in the opposite direction
    35
    previous, i.e. in direction F,
    40
    and through the elastic means 26 and 27 of circular action, the guide washers 17 are rotated. These guide washers in FIGS. 6-10 are fixed.
    Thus, when operating in the expansion mode, the hub 3, by means of its teeth 10 and 13, causes the counter-disk 6- to rotate, as shown by 45 arrows F, in FIG. 7 and 8.
    In the first phase (Fig. 7), only the elastic elements 26 are initially compressed, since the springs forming them have a relatively weak stiffness, in general, much weaker than the stiffness of the springs of the elastic elements 27.
    In the second phase (Fig. 8), the elastic elements 27 are also compressed, adding their action to the action of the elastic elements 26, which remain compressed.
    During the whole process, corresponding to the operation of the node in the mode
    50
    55
    previous, i.e. in direction F,
    and through the elastic means 26 and 27 of circular action, the guide washers 17 are rotated. These guide washers in FIGS. 6-10 are fixed.
    Thus, when operating in the expansion mode, the hub 3, with the help of its teeth 10 and 13, causes the counter-disk 6- to rotate, as indicated by the arrows F, in FIG. 7 and 8.
    In the first phase (Fig. 7), only the elastic elements 26 are initially compressed, since the springs forming them have a relatively weak stiffness, in general, much weaker than the stiffness of the springs of the elastic elements 27.
    In the second phase (Fig. 8), the elastic elements 27 are also compressed, adding their action to the action of the elastic elements 26, which remain compressed.
    During the whole process, corresponding to the operation of the node in the mode
    9
    the hub disk 5 is inactive due to the presence of the gap Jj and only the counter-disks 6 of the hub work.
    This process continues until parts 1 and 2 do not abut each other in the appropriate direction of rotation, either as a result of full compression of the elastic elements 26 and 27, or as a result of at least one of the axial links 18 abutting the corresponding edge of the holes 20 counterdisk 6, through which it passes.
    If at any moment during the transition from work in expansion mode to work in compression mode, the turning moment between parts 2 and 1 changes its direction and the torque becomes less than the opposing moment, the process is reversed as described, during which elastic elements 17, and then elastic elements 26. In practice, this softening occurs instantly.
    It corresponds to the reverse rotation of the hub 3 relative to the direction of the lower washers 17, indicated by the arrow of the РЗ in FIG. 3.
    When working in compression mode, when the whole node continues to rotate in





    the direction F as the car moves forward, the hub 3 rotates relative to the guide washers 17 in the opposite direction
    After installation in the initial position, the hub 3 causes the hub disk 5 to rotate in the direction. F (, done this with the help of his teeth 10 and 13,
    In the first phase (Fig. 9), the elastic elements 26 are compressed first.
    In the second phase (Figure 10), the elastic elements 27 are also compressed and their action is added to the action of the elastic elements 26, which remain compressed.
    During this entire process, the counterdisk 6 is inactive and there is a gap J (only the hub disk 5 is in operation. This process continues until parts I and 2 abut each other in the corresponding direction of rotation, or because at least one of the elastic members 26 and 27 is compressed again, or as a result
    ten
    0
    five
    0
    five
    0
    five
    0
    five
    0
    five
    the fact that at least one of the axial links 8 abuts against the corresponding edge of the holes 19 of the disk of the hub 5 through which it passes.
    In order to simplify the description, the phenomenon of hysteresis, which occurs when the angular deviation between parts I and 2 due to friction between,
    As is well known, this phenomenon of hysteresis leads, for a given angular ratio to the difference between the magnitude of the increasing torque and the magnitude of the decreasing torque. From this it follows that the gap J {must be greater than the gap Jg, which must be greater than the gap Jo ,.
    The present invention is not limited to the embodiment described and shown in the drawings. For example, if desired, the counterdisks of the hub can be interconnected during rotation by means of axial ligaments that pass with a gap through the disk of the hub to which they are connected,
    In addition, the number of coaxial parts rotatably mounted relative to each other and forming a shock absorber of torsional vibrations may be more than two.
    The scope of the invention is not limited to; friction clutches, it can, for example, extend to torsional vibration dampers without being equipped with any Friction discs, such shock absorbers are used as Vibration Filters B) continuous transmissions .
    权利要求:
    Claims (5)
    [1]
    Invention Formula
    i, Torsional vibration damper, predominantly for a car, containing at least two coaxial parts, mounted with the possibility of angular mixing relative to each other and interconnected by means of elastic elements, while one of the parts consists of a disk mounted on the hub with the possibility one-sided engagement, the second part consists of at least one guide washer installed with the possibility of angular. A hitch mixing with respect to a hub, characterized in that.
    in order to reduce noise and increase durability, it is equipped with at least one additional counter disk connected to the hub disk with elastic elements and mounted on the hub, with the possibility of one-sided engagement corresponding to the free position of the discs while the counter position is free corresponds to the engagement of the disc
    [2]
    2. Shock absorber pop, 1, the difference with the fact that the hub disk, counterdisk and washer direction are made with holes in which elastic elements are installed, and at least for one elastic element the holes in the disk of the hub, the counter disk and the ball of the washer have the same configuration, and for at least one other elastic element the holes
    V
    In the field of the hub and counterdisc, there are dimensions, larger holes in the guide, and an elastic element is installed in the disc holes, and a counterdisc with a gap.
    [3]
    3. The shock absorber according to claims 1 and 2, which is characterized by the fact that on the hub, hub disk and counter disk there are means of engagement in the form of teeth on the hub, grooves on the disk and counter disk,
    [4]
    4. The shock absorber on PP, 1-3, about t - the fact that it is equipped with two counter-disks installed on both sides of the hub disk,
    [5]
    5. The shock absorber according to claim, characterized in that the discs of the hub and counterdiscs have the same configuration.
    l - / t
    6 5 5 П
    / And
    50
    26
    Jz
    ;five
    20
    2Q
    LS
    eight
    Fie.2
    6-b
    3
    /
    about 48
    FIG. 6
    c-2018 fchg- 7
    l
    P :
    fyo
    类似技术:
    公开号 | 公开日 | 专利标题
    SU1600642A3|1990-10-15|Torsion oscillation absorber
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    US6209701B1|2001-04-03|Damper disk assembly
    KR960016600B1|1996-12-16|Torsion damping devices with large angular displacements such as automotive friction clutches
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    GB2235749A|1991-03-13|Friction clutch driven plate
    KR0174250B1|1999-02-18|Friction clutch driven plates
    US4838107A|1989-06-13|Vibration damping rotary drive element
    US4518071A|1985-05-21|Clutch disc having damper springs
    US4499981A|1985-02-19|Damper disc with concentric springs including hourglass-shaped springs to reduce the effect of centrifugal forces
    US5816925A|1998-10-06|Damper disk assembly, frictional coupling portion and clutch disk assembly
    JP2698237B2|1998-01-19|2-mass flywheel
    US5059155A|1991-10-22|Friction device of damper disc
    US5104356A|1992-04-14|Torsion damper, in particular a damped double flywheel for an automotive vehicle
    GB2220249A|1990-01-04|A torsion damping assembly, especially for an automotive vehicle
    EP1787039A1|2007-05-23|Clutch driven plate
    JP3408660B2|2003-05-19|Damper mechanism
    EP0414360B1|1994-11-09|Damper disc
    JPH0754922A|1995-02-28|Flywheel assembly
    JPH1130291A|1999-02-02|Damper gear and bearing locking method
    JP3556008B2|2004-08-18|Damper disk assembly
    同族专利:
    公开号 | 公开日
    FR2568642A1|1986-02-07|
    US4674992A|1987-06-23|
    JP2717783B2|1998-02-25|
    DE3566721D1|1989-01-12|
    EP0172100B1|1988-12-07|
    EP0172100A1|1986-02-19|
    JPS61105324A|1986-05-23|
    FR2568642B1|1990-06-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE4308289A1|1992-03-19|1993-09-23|Valeo|Damped car clutch disc with two coaxial parts - has flat zone on outer periphery extended by second elastic outer part radialin opposite direction to axis of unit|FR1411155A|1964-08-04|1965-09-17|Ferodo Sa|Improvements to damper hub clutch friction|
    FR2386729B1|1977-04-04|1980-02-01|Ferodo Sa|
    GB1565645A|1978-02-28|1980-04-23|Automotive Prod Co Ltd|Friction clutch driven plate|
    FR2492024B1|1980-10-15|1985-04-26|Valeo|
    FR2500557B1|1981-02-25|1985-06-14|Valeo|TORSION DAMPING DEVICE, IN PARTICULAR A CLUTCH FRICTION, IN PARTICULAR FOR A MOTOR VEHICLE|
    FR2503295B1|1981-04-01|1988-04-15|Automotive Prod France|FRICTION CLUTCH OUTPUT DISC|
    US4485908A|1982-06-09|1984-12-04|Borg-Warner Corporation|Vibration damper with variable rate springs and damping friction|
    JPH0340252B2|1982-10-14|1991-06-18|
    JPS59125393A|1983-01-06|1984-07-19|Matsushita Electric Ind Co Ltd|Safety device of latent heat accumulator|
    JPH027291Y2|1983-02-09|1990-02-21|DE3721711C2|1986-07-05|1997-09-04|Luk Lamellen & Kupplungsbau|Device for damping vibrations|
    JPH0648016B2|1986-07-10|1994-06-22|三菱自動車工業株式会社|Multi-stage clutch|
    DE3637383C2|1986-11-03|1990-02-15|Viscodrive Gmbh, 5204 Lohmar, De|
    DE3737787A1|1986-11-28|1988-06-09|Dana Corp|DEVICE FOR TRANSMITTING A TORQUE|
    FR2609771B1|1987-01-19|1991-03-22|Valeo|LOCKING ASSEMBLY FOR A HYDROKINETIC APPARATUS AND A HYDROKINETIC APPARATUS COMPRISING SUCH A LOCKING ASSEMBLY, PARTICULARLY FOR A MOTOR VEHICLE|
    GB8708536D0|1987-04-09|1987-05-13|Automotive Prod Plc|Torsional vibration damper|
    FR2624236B1|1987-12-08|1990-04-06|Valeo|TORSION DAMPING DEVICE WITH LARGE ANGLE TRAVEL, ESPECIALLY CLUTCH FRICTION, ESPECIALLY FOR A MOTOR VEHICLE|
    US5161660A|1990-11-15|1992-11-10|Luk Lamellen Und Kupplungsbau Gmbh|Clutch plate with plural dampers|
    JPH05296290A|1992-04-17|1993-11-09|Aisin Seiki Co Ltd|Torsional vibration damping device|
    US5505288A|1993-10-07|1996-04-09|Kabushiki Kaisha Daikin Seisakusho|Damper disc assembly|
    JP2006188153A|2005-01-06|2006-07-20|Toyota Motor Corp|In-wheel motor|
    CN101641531B|2007-03-19|2011-11-16|舍弗勒技术两合公司|Torsional vibration damper|
    JP5234223B1|2011-09-22|2013-07-10|トヨタ自動車株式会社|Torsional vibration damping device|
    DE102012214022A1|2012-08-08|2014-02-13|Schaeffler Technologies AG & Co. KG|Torsional vibration damper i.e. disk damper, for use in clutch disk of starting clutch of motor vehicle, has output flange coupled with another output flange over friction disk, where disk has internal gear for coupling with input shaft|
    JP2016536529A|2013-09-24|2016-11-24|シェフラー テクノロジーズ アー・ゲー ウント コー． カー・ゲーＳｃｈａｅｆｆｌｅｒ Ｔｅｃｈｎｏｌｏｇｉｅｓ ＡＧ ＆ Ｃｏ． ＫＧ|Series-to-parallel damper assembly with flange|
    FR3039237B1|2015-07-24|2018-03-02|Valeo Embrayages|TORQUE TRANSMISSION DEVICE FOR A MOTOR VEHICLE|
    FR3039235B1|2015-07-24|2019-04-12|Valeo Embrayages|VIBRATION DAMPING DEVICE|
    CN113557370A|2019-07-01|2021-10-26|舍弗勒技术股份两合公司|Clutch driven plate and clutch|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    FR8412293A|FR2568642B1|1984-08-03|1984-08-03|TORSION DAMPING DEVICE WITH LARGE ANGLE TRAVEL, ESPECIALLY CLUTCH FRICTION, ESPECIALLY FOR A MOTOR VEHICLE|
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