• 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:
    1504011 Mounting clutch plates on hubs LUK LAMELLEN UND KUPPLUNGSBAU GmbH 22 July 1975 [27 July 1974] 30661/75 Heading F2U A clutch plate 1 to 3 is resiliently mounted on a hub 5 having fixed plates 4, 6 spaced apart to form a gap for a resiliently-loaded friction device 8 to 12 which is inoperative over an initial range and operable over a further range of relative movement between the clutch plate and hub. The plate 6 is fixed to the hub plate 4 by rivets and the counter-plate 3 is fixed to the clutch plate 1 by rivets 2, 2<SP>1</SP> and 2<SP>11</SP>. Further friction devices are also provided to act throughout the ranges of movement, these being friction plates 18, 21 loaded by a spring 19 and washer 20. The friction device 8 to 12 consists of friction plates 9, 10, a spring 11, an intermediate plate 12 engaging the plate 6 by a projection 12a and a friction plate 8 which has radial arms embracing a pair of helical springs 14 and end plates 14a of the springs. In the drawings A is the traction direction and B the opposite direction in which the road wheels drive the engine. Over the range A 1 (or B 1 ) only the helical spring 15 is effective (besides the friction plates 18, 21). From A 1 to A 2 the effect of the spring 16 is added to spring 15 while the friction plate 8 is carried around by the friction plates 9, 10. From A 2 to A 3 the rivet 2<SP>1</SP> acts on the friction plate 8 to compress the pair of springs 14. From A 3 to A 4 the effect of a pair of springs 17 is added to the limit provided by abutment of the rivet 2<SP>11</SP> in hub plate aperture 31. All the helical springs are assembled in a prestressed condition. In a second embodiment, Fig. 5 (not shown), the friction device (44) is disposed in the gap between end plates (41) riveted to the hub (40) and the friction plate 8 is replaced by a pair of plates (45). In a third embodiment, Fig. 6 (not shown), the friction device (67) is disposed in the gap between end plates (64), and the friction plate 8 is replaced by a friction plate (68).
    公开号:SU1085514A3
    申请号:SU782617556
    申请日:1978-05-18
    公开日:1984-04-07
    发明作者:Маухер Пауль
    申请人:Люк Ламеллен Унд Купплюнгсбау Гмбх (Фирма)；
    IPC主号:
    专利说明:

    2. A clutch disc according to claim 1, characterized in that the hub discs are mounted with the windows of the same configuration, facing each other, and the elastic elements are placed in them.
    3. Coupling disk according to claims 1 and 2, characterized in that the friction disk is provided with an additional disk, the friction element of the load device is located between them and interacts with them through the pads, the friction element and the friction disk are made with windows, and the elastic elements located in them and in contact with the bearing disks of the sleeve and the friction disk.
    4. Coupling disk according to claims 1, 1-3, characterized in that
    it is provided with a stop fixed on the sleeve and bounding the rotation of the friction element of the loading device relative to the tulk and.
    5. Coupling disk according to paragraphs 1-4, characterized in that the friction disk and the friction element of the loading device are made with arc grooves, and the stop is in the form of a rod rigidly fixed in them with ends
    on the carrier discs of the sleeve, in this case, the length of the arc groove of the friction disk is equal to the size of its movement in the circumferential direction, and the length of the arc groove of the friction element of the load device is less than the length of the arc groove of the friction disk.
    6. The clutch disc according to claims 1-5, characterized in that it is equipped with an additional disc rigidly fixed to the friction
    disk with an axial gap, and the load device is placed in this gap.
    7. Coupling disk according to claims 1-6, characterized in that one part of the elastic elements is in contact with the loading device, the vom and carrier disks of the bushings, and
    other - with a load device and a friction disk.
    8. Coupling disk according to claims 1-6, characterized in that the elastic elements are installed in the windows of the friction element of the loading device with a preliminary
    .
    9. The clutch disc according to claim 8, in which the length of the friction disk windows and the carrier disks of the hub is equal to the length of the windows of the friction element of the load device.
    10. Clutch disc according to claims 1-7, characterized in that
     the length of the windows of the friction disk is longer than the free length of the elastic elements
    11. The clutch disc according to claims 1-7, except that
    the length of the windows of the bearing discs of the sleeve is largely the free length of the elastic elements.
    12. The clutch disc according to claims 1-7, which is distinguished by the fact that
    the length of the windows of the friction element of the load device is greater than the free length of the elastic elements.
    13. Coupling disk according to claims 1-3, characterized in that the support is rigidly fixed to the loading device.
    14. The clutch disc according to claim 13, characterized in that the loading device is made
    in the form of two friction elements rigidly connected to each other and located on both sides of the friction disk.
    15. Coupling disk according to claim 14, which is characterized by the fact that the friction disk is made with openings, and the stop is in the form of a rod located in them, rigidly fixed by the ends of the loading device on the friction elements.
    16. A clutch disc according to claim 14, which is different in that the arc size of the windows of the friction disk is larger than the arc size of the windows of the friction element of the load device.

    The invention relates to mechanical engineering, in particular to devices for transmitting rotation.
    Closest to the invention is a clutch disc containing sleeve c. rigidly fixed on it bearing discs and friction
    a disk with overlays located between said carrier disks with the possibility of angular rotation and associated with them through elastic elements l.
    A disadvantage of the known clutch disc is low reliability. The aim of the invention is to increase the reliability of operation by increasing the transmitted torque when switching on. This goal is achieved by the fact that the clutch disc, mainly for automobiles, is equipped with a loading friction device located in the axial gap between the bearing discs and made in the form of a friction element, damping plates and elastic elements in contact with the friction element. Bearing disks of the bushings are made with windows of the same configuration, arranged against each other, and elastic elements are placed in them. The friction disk is provided with an additional disk, the friction element of the loading device is located between them and interacts with them through the lining, while the friction element of the loading device and the friction disk are made with windows, and the elastic elements are located in them and contact with the bearing bushings and friction disk. Dissipation is provided with a stop, n movably mounted on the sleeve and limiting the rotation of the friction element of the load device relative to the sleeve. The friction disk and the friction element of the load device are made with arc grooves, and the stop is in the form of a rod rigidly fixed in them with ends of carrier disks of the sleeve, while for the arc groove of the friction disk it is equal to its displacement in the circumferential direction, and the arc groove length of the friction element of the load device, the smaller lengths of the arc groove of the friction disk The clutch disk is equipped with an additional disk rigidly fixed on the friction disk with an axial gap, and the load device placed in the gap. One part of the elastic elements is in contact with the load device and the carrier discs of the sleeve, and the other part is connected with the load device and the frictional Hbw disk. Elastic elements are installed in the windows of the friction element of the load device with preliminary preload. The length of the windows of the friction disk and the carrier discs of the sleeve is equal to the length of the windows of the friction element of the load device. The length of the windows of the friction disk is greater than the free length of the elastic elements. The length of the windows of the carrier discs of the sleeve is greater than the free length of the elastic elements. The length of the windows of the friction element of the load device is greater than the free length of the elastic elements. The stop is rigidly fixed on the load device. The load device is made in the form of two friction elements rigidly connected to each other and located on both sides of the friction disk. The friction disk is made with holes, and the stop is in the form of a rod rigidly fixed in them with ends on the friction elements of the load device. The arc size of the windows of the friction disk is larger than the arc size of the windows of the friction element of the load device. Fig. 1 shows a clutch disc; Fig. 2 shows a clutch disc; Fig. 3 is a graph showing the change in the magnitude of the transmitted moment. The clutch disc contains a sleeve 1 and two carrier disks 2 rigidly attached to it, as well as a friction disk 3 with overlays 4, which can be inserted relative to the sleeve 1 and placed in a space located in the axial direction between the disks 2. In the axial intermediate space between The disks 2 together with the friction disk 3 are provided with a friction-loading device 5 consisting of two friction elements in the form of rings 6, which circumferentially surround the sleeve 1, are connected to each other through the stop 7 and have a friction The pads 8 and the slip pads 9, loaded in the axial direction by the cup-shaped spring 10. The circumferentially displaced elastic elements 11 are made in the form of springs and are located in the windows 12 of the carrier disks 2, the windows 13 of the rings biv windows 14 of the friction disk 3. In addition, there are friction damping pads 15 and 16, pressed along the axis by a wavy spring 17 to the friction disk 3. The stop 7 passes through the arc groove 18 of the friction disk 3, and its length in the direction of the circumference allows the friction disk 3 to rotate at the same time Onno-load device 5 no. acts as the rings b do not turn, rotate relative to the sleeve. The springs 11 are located in the windows 12, which may have the same length in the tangential direction.
    The friction disk 3 has windows, the potential length of which could be longer than the length of the spring 11.
    At the end of the turn, friction damping plates 15 and 16 act on the friction disk, the moment of their friction is greater than the moment of training the lining 9.
    After selecting a gap in the arc groove 18, the friction disk 3 contacts with the stop 7 and rotates the ring 6. At the same time, they, together with the friction clutches with the overlays 9, transfer the force to the sleeve 1. The springs 11 can be installed in the windows 13 of the rings 6. The tangential length of the windows 12, the disk 2 and the friction disk 3 may be greater than the free length of the springs.
    At the end of the rotation of the friction disc, all the springs act. One or more springs 11 can be installed in the windows 12 and 14 with tension.
    The springs of the proposed clutch disc do not rotate with respect to the body of the sleeve. However, it is possible to imagine such an embodiment, according to which, for example, the spring 11 initially does not work and rotates with respect to the sleeve 1, since it is installed in the corresponding window 14 with prestressing. In this case, the windows of the disk 2 and the rings b allow some twisting of the friction disk and, in accordance with the desired damping characteristics, it is possible to choose windows 14 that are smaller than windows in rings 6.
    According to another variant of the clutch disc, the friction disc 3, a non-admission pad, is located in the intermediate space axially between the two carrier discs 2 and contains an additional disc 19 which has the overlays 20 and is rigidly connected to the disc 3 through a rivet 21. In the space located along the axes between the side discs 2, friction-loading device 22, which consists of a friction disk 23 covering the sleeve circumferentially and friction linings 24, are also provided. Unlike the first variant, the friction-loading device roystvo to the extent of rotation in which it does not act, it is rotated together with the disk 3 and comes into operation at the end of its rotation relative to the hub 1
    The friction damping pads 24 are tightened axially by the disk 25, and the friction lining 2 is loaded axially with a buckle spring 27.
    The group of springs 11, placed in the direction of the circle, is located in the windows 28 and in the disks 2 in the corresponding group of windows 12 and 29.
    The rivet g-stop 30, which connects both discs with one another, serves primarily as a stop, coming into action, the field of overcoming the initial angle of rotation.
    To obtain a flat line characterization with relative rotation of the friction disk 3 with respect to sleeve 1, the end turns of the spring 11 in the initial position abut against the ends of windows 28 and 12. For the final area of the rotation, there is also a spring 11 held in the same window size 28. Windows 12 . are made longer in the direction of the circumference by the allowable angle of rotation of the size of the window 28. At the end of the rotation, friction lining 26 and lining 20 act. For springs 11, friction disk 23 has windows that have the same size as windows 12 in disks 2, or greater than this value.
    At the end of the rotation, the wall of the opening 31 of the disk 23 pushes the stop 30, which, when turning angles higher than normal, the disk 23 stops and in addition to the action of the friction linings 26, the action of the friction linings 20 is added.
    In addition, springs 11 can be installed, which are mounted in windows 12 and 28 having a tangential length. At the end of the rotation, these springs in both directions of rotation are in contact with the walls of these holes and compressed.
    The reverse rotation of the friction disk 3 is performed by one or several springs 11, while if one spring is working, either window 12 should be made according to its length or larger.
    The return of parts 19 and 23 to the initial position is performed by the springs 11, and the pre-stress in the initial position must be chosen at least the same size as the moment of friction lining friction training.
    Spaufatcuttftf ftoftfftm
    Bpautafoufvu ftofteffOf
    权利要求:
    Claims (14)
    [1]
    1. CLUTCH VISIT, PREVIOUSLY FOR CARS, comprising a sleeve with bearing discs rigidly fixed on it and a friction disk with overlays located between the bearing discs with the possibility of angular rotation and connected with them and through elastic elements, characterized in that, for the purpose to increase the reliability of work by ensuring an increase in the transmitted moment, it is equipped with a friction loading device located in the axial clearance between the bearing disks and made in the form of a friction element damping Dock and elastic elements in contact with the friction element _ ment. § £
    FIG. 1
    [2]
    2. The clutch disc according to claim 1, o t = characterized in that the bearing discs of the sleeve are made with windows of the same configuration, located opposite each other, and the elastic elements are placed in them.
    [3]
    3. The clutch disc according to claims 1 and 2, characterized in that the friction disc is equipped with an additional disc, the friction element of the load device is located between them and interacts with them through the linings, while the friction element and the friction disc are made with windows, and elastic elements are located in them and are in contact with the bearing discs of the sleeve and the friction disk.
    [4]
    4. The clutch disc according to claims 1 to 3, characterized in that it is provided with a stop fixedly mounted on the sleeve and restricting the rotation of the friction element of the loading device relative to the sleeve.
    [5]
    5. The clutch disc according to claims 1 to 4, characterized in that the friction disk and the friction element of the load device are made with arc grooves, and the emphasis is in the form of a rod located in them, rigidly fixed by the ends on the bearing disks of the sleeve, wherein: the length of the arc the groove of the friction disk is equal to its displacement in the circumferential direction, and the length of the arc groove of the friction element of the load device is less than the length of the arc groove of the friction! th disk.
    [6]
    6. The clutch disc according to claims 1-5, characterized in that it is equipped with an additional disc, rigidly mounted on a friction disc with an axial clearance, and the load device is placed in this gap.
    [7]
    7 '. The clutch disc according to claims 1 to 6, characterized in that one part of the elastic elements is in contact with the load device and the bearing discs of the sleeve, and the other with the load device and the friction disk.
    [8]
    8. The clutch disc according to claims 1 to 6, characterized in that the elastic elements are installed in the windows of the friction element of the load device with preliminary • preload.
    [9]
    9. The clutch disc of claim 8, wherein the length of the windows of the friction disc and the bearing discs of the sleeve is equal to the length of the windows of the friction element of the load device.
    [10]
    10. The clutch disc according to claims 1 to 7, characterized in that the window length of the friction disc is greater than the free length of the elastic elements,
    [11]
    11. The clutch disc according to claims 1 to 7, ex. characterized in that the length of the windows of the bearing disks of the sleeve is greater than the free length of the elastic elements.
    [12]
    12. The clutch disc according to claims 1 to 7, characterized in that the window length of the friction element of the load device is greater than the free length of the elastic elements.
    13. Clutch disc paragraphs 1-3, about t l and h s I the fact that emphasis is tough fixed on the stressful device 14· Disk clutch by p. 13, about t l and h s I the fact that load device performed in form two frictional elements
    rigidly interconnected and located on both sides of the friction disk.
    [13]
    15. The clutch disc according to item 14, characterized in that the friction disc is made with holes, and the emphasis is in the form of a rod located in them, rigidly fixed by the ends to the friction elements of the load device.
    [14]
    16. The clutch disc according to 14, characterized in that the arc size of the windows of the friction disk is larger than the arc size of the windows of the friction element of the load device.
    类似技术:
    公开号 | 公开日 | 专利标题
    SU1085514A3|1984-04-07|Friction clutch,preferably for automobile vehicles
    US5139124A|1992-08-18|Apparatus for compensating for fluctuations of torque between the engine and the transmission of a motor vehicle
    JP2891706B2|1999-05-17|Shock absorber for absorbing or compensating torsional impacts, especially torque fluctuations in internal combustion engines
    US3428155A|1969-02-18|Clutch plate with vibration dampeners in series
    US3800931A|1974-04-02|Clutch disc
    US5073143A|1991-12-17|Apparatus for transmitting torque between the engine and the change speed transmission of a motor vehicle
    US4596535A|1986-06-24|Friction mechanism in a damper disc
    US4274525A|1981-06-23|Clutch disc
    US5725080A|1998-03-10|Clutch for motor vehicles having a clutch disc with spring elements connected in series
    JP2708058B2|1998-02-04|Damper device
    US4368812A|1983-01-18|Clutch plate
    US4093054A|1978-06-06|Belleville damper for torque transmitting coupling device
    US4846759A|1989-07-11|Device for reducing engine-excited vibrations of a drive train, especially a split flywheel
    US4889009A|1989-12-26|Torque transmitting mechanism
    US4177888A|1979-12-11|Friction clutch plate with two concentric hubs for damping
    US4789375A|1988-12-06|Spring damper drive for a clutch driven disc assembly
    US5176233A|1993-01-05|Apparatus for reducing vehicle drive train vibrations
    US4210234A|1980-07-01|Torsional vibration damper
    US5884743A|1999-03-23|Clutch plate with centering feature
    US3375911A|1968-04-02|Clutch plate employing torsion damper
    US5456634A|1995-10-10|Torsion damping apparatus for use with friction clutches in the power trains of motor vehicles
    US4499981A|1985-02-19|Damper disc with concentric springs including hourglass-shaped springs to reduce the effect of centrifugal forces
    US4895237A|1990-01-23|Component for use in the power train of a motor vehicle
    JPH08507355A|1996-08-06|Damping device that can be integrated with a power unit of an automobile
    US3039578A|1962-06-19|Clutches
    同族专利:
    公开号 | 公开日
    JPS5141159A|1976-04-06|
    US4122931A|1978-10-31|
    JPS5874920A|1983-05-06|
    JPS5928777B2|1984-07-16|
    FR2279973A1|1976-02-20|
    DE2436288B2|1977-03-03|
    US4381052A|1983-04-26|
    GB1504011A|1978-03-15|
    DE2436288A1|1976-02-05|
    SU843782A3|1981-06-30|
    FR2279973B1|1978-12-29|
    JPS5952297B2|1984-12-19|
    BR7504766A|1976-07-06|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    FR1411155A|1964-08-04|1965-09-17|Ferodo Sa|Improvements to damper hub clutch friction|
    DE1475346B1|1965-12-01|1970-05-14|Fichtel & Sachs Ag, 8720 Schweinfurt|Clutch disc with several vibration dampers connected in series|
    FR1520684A|1967-03-02|1968-04-12|Ferodo Sa|Improvements to the clutch friction discs with damper hubs|
    FR1572343A|1968-04-09|1969-06-27|
    US3684070A|1970-04-21|1972-08-15|Paul Maucher|Clutch disc|
    DE2029356C3|1970-06-15|1974-07-18|Fichtel & Sachs Ag, 8720 Schweinfurt|Clutch disc with torsion damper with a characteristic curve that is dependent on the direction of rotation|
    FR2162702A5|1971-11-29|1973-07-20|Ferodo Sa|
    IT994549B|1972-08-03|1975-10-20|Fichtel & Sachs Ag|CLUTCH DISC|
    FR2217599B1|1973-02-12|1977-09-02|Ferodo Sa|
    DE2338394C2|1973-07-28|1975-05-22|Daimler-Benz Ag, 7000 Stuttgart|Clutch disc for motor vehicle main clutches|DE7538331U|1975-12-02|1976-05-26|Fichtel & Sachs Ag, 8720 Schweinfurt|CLUTCH DISC WITH TWO-STAGE FRICTION|
    US4188805A|1977-05-31|1980-02-19|Borg-Warner Corporation|Torsional vibration damper|
    FR2449828B1|1979-02-23|1983-04-01|Ferodo Sa|
    US4269296A|1979-06-27|1981-05-26|Flotow Richard A|Two-stage coaxial spring damper|
    WO1981001731A1|1979-12-13|1981-06-25|W Windish|Torsional vibration damper assembly|
    US4318283A|1979-12-13|1982-03-09|Caterpillar Tractor Co.|Torsional vibration damper assembly|
    JPS6151172B2|1980-02-06|1986-11-07|Daikin Mfg Co Ltd|
    US4401201A|1980-12-22|1983-08-30|Borg-Warner Corporation|Clutch driven plate assembly|
    DE3126695C2|1981-07-07|1991-04-25|Luk Lamellen Und Kupplungsbau Gmbh, 7580 Buehl, De|
    DE3136600A1|1981-09-15|1983-03-31|LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl|CLUTCH DISC|
    EP0079727B1|1981-11-14|1985-10-09|Automotive Products Public Limited Company|Friction clutch driven plate|
    DE3147237C2|1981-11-28|1991-11-21|Luk Lamellen Und Kupplungsbau Gmbh, 7580 Buehl, De|
    US4485909A|1982-06-14|1984-12-04|Borg-Warner Corporation|Multiple stage vibration damper|
    US4618048A|1982-06-29|1986-10-21|Aisin Seiki Kabushiki Kaisha|Clutch disk assembly|
    DE3227004C2|1982-07-20|1990-10-04|Fichtel & Sachs Ag, 8720 Schweinfurt, De|
    DE3230663C2|1982-08-18|1986-02-27|Fichtel & Sachs Ag, 8720 Schweinfurt|Clutch disc with torsional vibration damper and control plate|
    DE3248119C2|1982-12-24|1992-03-12|Luk Lamellen Und Kupplungsbau Gmbh, 7580 Buehl, De|
    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|
    JPH0242133B2|1983-12-22|1990-09-20|
    DE3405949C2|1984-02-18|1992-07-23|Fichtel & Sachs Ag, 8720 Schweinfurt, De|
    JPS60192124A|1984-03-09|1985-09-30|Daikin Mfg Co Ltd|Friction device for damper disc|
    DE3415926C2|1984-04-28|1992-07-23|Fichtel & Sachs Ag, 8720 Schweinfurt, De|
    US5180335A|1984-06-12|1993-01-19|Luk Lamellen Und Kupplungsbau Gmbh|Torsion damping assembly for use with clutches in motor vehicles|
    DE8521345U1|1985-07-24|1985-10-03|Fichtel & Sachs Ag, 8720 Schweinfurt|Clutch disc with torsional vibration damper and concentrically arranged torsion springs|
    DE3528662C2|1985-08-09|1994-12-08|Fichtel & Sachs Ag|Torsional vibration damper with concentrically arranged springs|
    JPS63115915A|1986-11-03|1988-05-20|Uni Cardan Ag|Clutch disk|
    DE68910769T2|1988-09-29|1994-03-24|Aisin Seiki|Clutch disc.|
    DE19654970C2|1996-08-05|2002-02-21|Mannesmann Sachs Ag|torsional vibration damper|
    DE10148435A1|2001-10-01|2003-04-17|Zf Sachs Ag|Friction clutch, in particular multi-disc clutch|
    JP4747875B2|2006-02-16|2011-08-17|アイシン精機株式会社|Torque fluctuation absorber|
    CN202301693U|2011-10-27|2012-07-04|比亚迪股份有限公司|Multi-stage shock absorber structure and clutch with same|
    CN105202051A|2015-10-20|2015-12-30|无锡格莱德科技有限公司|Automobile clutch disk structure|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE19742436288|DE2436288C3|1974-07-27|Clutch disc|
    [返回顶部]