EP1216365A1 - Disques d'embrayage pour embrayages a friction - Google Patents

Disques d'embrayage pour embrayages a friction

Info

Publication number
EP1216365A1
EP1216365A1 EP01949747A EP01949747A EP1216365A1 EP 1216365 A1 EP1216365 A1 EP 1216365A1 EP 01949747 A EP01949747 A EP 01949747A EP 01949747 A EP01949747 A EP 01949747A EP 1216365 A1 EP1216365 A1 EP 1216365A1
Authority
EP
European Patent Office
Prior art keywords
driven plate
hub
main
pairs
opposed surfaces
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP01949747A
Other languages
German (de)
English (en)
Inventor
Alastair John Young
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Automotive Products PLC
Original Assignee
Automotive Products PLC
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Automotive Products PLC filed Critical Automotive Products PLC
Publication of EP1216365A1 publication Critical patent/EP1216365A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/1207—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by the supporting arrangement of the damper unit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs

Definitions

  • the present invention relates to driven plates for friction clutches.
  • the invention relates to driven plates for friction clutches in motor vehicles.
  • Known driven plates for friction clutches comprise a main driven plate assembly including at least one friction lining and a central hub for connection with a shaft- the main assembly being mounted concentrically about and drivingly connected to the hub
  • Such known driven plates are hereinafter referred to as driven plates of the type described.
  • Driven plates of the type described are often used in friction clutches for motor vehicles to selectively transfer drive from a flywheel, which may be attached to the crankshaft of an internal combustion engine, to a drive shaft of the vehicle transmission.
  • Such known friction clutches typically comprise a clutch cover assembly attached to the flywheel with the driven plate located between the clutch cover assembly and the flywheel
  • the clutch cover assembly comprises a pressure plate which is biased axially towards the flywheel when the clutch is engaged to clamp the friction linings of the driven plate between the pressure plate and the flywheel so that drive is transmitted from the flywheel to the driven plate and then via the hub to the transmission drive shaft.
  • driven plates of the type described for the main driven plate assembly to be drivingly connected to the hub by means of inter-engaging drive formations which have limited radial and circumferential clearances to allow the main assembly to move radially and circumferentially relative to the hub to a limited extent.
  • Such driven plates may comprise a torsion damper to isolate the drive line from vibrations generated in the engine.
  • driven plates of the type described may be of the rigid type in which no torsion damper is provided and the main driven plate assembly is fixed rotationally fast with, or is integral with, the central hub.
  • Such rigid driven plates are often used in conjunction with twin mass flywheels which comprise a torsion damper to isolate the drive line from vibrations generated by the engine.
  • the forces acting on the crankshaft of the engine may cause the flywheel to swash or swirl about the axis of the crankshaft.
  • the friction linings will tend to follow the movement of the flywheel and so will swash or swirl about the hub which is constrained to rotate about the axis transmission drive shaft. This again sets up cyclical stresses in the driven plate.
  • An object of the invention is to provide an improved driven plate of the type described which overcomes or at least mitigates the problems of the known driven plates.
  • a driven plate of the type described in which the mam driven plate assembly is drivingly connected with the hub by means of mter-engagmg drive formations which have limited radial and circumferential clearances to allow the ma assembly to move radially and circumferentiallv relative to the hub to a limited extent, the d ⁇ ven plate also having two pairs of opposed surfaces, each pair of opposed surfaces comprising a first surface associated with the hub and a second surface associated with the mam d ⁇ ven plate assembly w th at least one of the surfaces m each pair bemg inclined obliquelv to the axis of the driven plate, one of the pairs of opposed surfaces acting to inhibit movement of the mam driven plate assembly relative to the hub m a first axial direction of the d ⁇ ven plate, the other of the pairs acting to inhibit movement of the mam driven plate assembly relative to the hub
  • the mam d ⁇ ven plate assembly is able to tilt relative to the hub in a controlled manner to allow the friction linings to rotate about an axis which is not angularlv aligned with the axis of rotation of the hub and/or to allow the friction linings to follow the swashing movement of a flvwheel without setting up stresses m the driven plate
  • the relative tiltmg between the ma driven plate assemblv and the hub can be controlled m a manner which does not generate a factional force between the surfaces so ensuring that mam driven plate assembly and hub can tilt freely relative to one another
  • Figure 1 is a cross sectional view of a d ⁇ ven plate m accordance with the mvention
  • Figure 2 is an enlarged v ew of a detail of Figure 1
  • Figure 3 is a view similar to Figure 2 showing a modification to the driven plate of Figure i;
  • Figure 4 is a cross sectional view of a second embodiment of a driven plate in accordance with the invention.
  • Figure 5 is an enlarged view of a detail of Figure 4.
  • Figure 6 is a view similar to that of Figure 5 showing a modification to the driven plate of Figure 4;
  • Figure 7 is a cross sectional view of a third embodiment of a driven plate in accordance with the invention.
  • Figure 8 is a view similar to that of Figure 7 showing a modified version of the driven plate of Figure 7
  • FIGS 1 and 2 show a driven plate 10 for use in a friction clutch for a motor vehicle.
  • the drive plate 10 comprises a main driven plate assembly 1 1 mounted on a central hub 12
  • the hub 12 has internal splines 13 for connection with a gearbox input shaft and an annular array of circumferentially spaced teeth 14 extending radially outwards from the outer surface of the hub.
  • the main driven plate assembly 1 1 is mounted co-axially about the hub 12 and comprises an annular flange 20 having an array of circumferentially spaced teeth 21 which extend radially inwardly from an inner periphery of the annular flange 20 for engagement with the teeth 14 on the outer surface of the hub 12 Limited circumferential and radial clearances are provided between the teeth 14 on the hub 12 and the teeth 21 on the flange 20 so that the flange 20 is able to move radially and circumferentially relative to the hub 12 to a limited extent
  • a first side plate 17 is arranged on the on the right hand side (as viewed in Figure 1 ) of the annular flange 20 whilst a second side plate 18 is arranged on the left hand side (as viewed in Figure 1) of the annular flange 20.
  • the first and second side plates 17. 18 are rigidly connected by means of a number of rivets 19 which pass through corresponding openings 20a in the annular flange 20.
  • the second side plate 18 carries a pair of friction linings 15 which are mounted to the side plate via spring segments 16.
  • the side plates 17, 18 are capable of limited rotational movement relative to the annular flange 20 and a set of main torsion damping springs 22 are housed in aligned apertures 23 and 24 m the annular flange 20 and the side plates 17,18 respectively, to control the rotational movement therebetween
  • a set of main torsion damping springs 22 are housed in aligned apertures 23 and 24 m the annular flange 20 and the side plates 17,18 respectively, to control the rotational movement therebetween
  • the number of springs 22 used is not essential and more or less than six can be used as required
  • the springs 22 may each comprise two separate sp ⁇ ngs, one arranged concent ⁇ cally inside the other
  • the relative rotational movement between the side plates 17, 18 and the annular flange 20 is also controlled by a friction damper 25
  • the friction damper comprises first and second friction washers 26,27 (see figure 2) arranged between the second s de plate 18 and the annular flange 20 and a third friction washer 28 located between the annular flange 20 and the first side plate 17
  • a sp ⁇ ng washer 29 acts between the third friction washer 28 and the first side plate 17 to clamp the friction washers the annular flange and the second s de plate together so that rotational movement of the side plates 17. 18 relative to the annular flange 20 results m the generation of a friction damping force a manner known m the art
  • the d ⁇ ven plate also has a torsion pre-damper 30 to control the circumferential and radial movement permitted between the annular flange 20 and the hub due to the circumferential and radial clearances between the teeth 14 and 21
  • the pre-damper 30 comprises four circumferentialh equi-spaced springs 31 which are arranged enlarged spaces between consecutive teeth 14 and 21 on the hub 12 and annular flange 20 respectively
  • the springs 31 are aligned generally tangential to a pitch circle drawn concent ⁇ c with the axis of the d ⁇ ven plate and serve to oppose the circumferential and radial movement of the annular flange 20 relative to the hub 12 in a manner well known m the art
  • the driven plate has two pairs of opposed surfaces 32, 33 and 34 35 respectively Each pair comprises a first surface 32, 34 associated with the hub 12 and a second surface 33, 35 associated with the ma d ⁇ ven plate assembly 1 1
  • the first surfaces 32, 34 are each provided on a respective annular bearing ring 36, 37 which are located about the outer periphery of the central hub whilst the second surfaces 33, 35 are each provided on a splayed out portion of the radially inner peripheries of the side plates 17 and 18 respectively
  • One of the pairs of opposed surfaces 32, 33 is provided on the right hand (as viewed m Figure 2) axial side of the d ⁇ ven plate whilst the other pair of opposed surfaces 34, 35 is provided on the opposite (left hand, as viewed) axial side of the d ⁇ ven plate
  • Each of the pairs of opposed surfaces 32, 33 and 34, 35 are arranged generally at an oblique angle to the axis of the hub 12 and the arrangement is such that one of the pairs of opposed surfaces
  • the profile or shape of the surfaces 32, 33 and 34, 35 is such that the ma d ⁇ ven plate assembly 1 1 can tilt relative to the axis of the hub 12 as indicated by the arrows W (see Figure 1), with the first and second surfaces in each pair sliding relative to each other
  • the first surfaces 32. 34 are both part-spherical with the surface 32 having a centre X located on the axis of the hub 12 whilst the surface 34 has a centre Y also located on the axis of the hub 12
  • the profiles of the second surfaces 33, 35 are such as to generally conform with the profiles of their respective first surfaces 32, 33
  • a small working clearance may be provided between each pair of opposed surfaces 32, 33 and 34, 35 so that the main d ⁇ ven plate assembly 1 1 is able to freely tilt about the axis of the hub 12
  • the total working clearances between the surfaces 32. 33 and 34, 35 may be in the order of 0 05 to 0 5 mm
  • the opposed surfaces in each pair are not biased m to contact with each other so that factional resistance is kept to a minimum
  • the friction damper 25 is loaded between the two side plates 17 and 18 and does not produce any loading between the opposed surfaces 32, 33 and 34, 35
  • the bearing rings 36 and 37 can be made from any suitable material but preferably they are made from a plastics material having a relatively low coefficient of friction so that the opposed surfaces 32, 33 and 34, 35 slide freely over each other to further ensure that the ma d ⁇ ven plate assembly 1 1 can tilt easily relative to the hub 12
  • the bearing rings 36, 37 may each have projections 40 which engage with the teeth 14 on the hub 12 to ensure that the rings rotate with the hub 12 It should be understood that the invention is not limited to the arrangement disclosed in the embodiment shown in Figures 1 and 2 in which the first surfaces 32, 34 are part spherical and the second surfaces 33, 35 conform generally to the profile of their respective first surfaces.
  • the invention embraces any arrangement in which the two pairs of opposed surfaces 32, 33 and 34, 35 permit relative tilting or pivotal movement between the main driven plate assembly 11 and the central hub 12.
  • the first surfaces 32, 34 could be spherical or part-spherical with a common centre, they could be conical or part- conical, tapered, contoured, or may have a radius which is not spherical, they could be convex or concave.
  • the opposed surfaces 32, 33 and 34, 35 in each pair need not fully conform in profile with each other in order for the invention to be applied. Indeed it is sufficient for the surfaces 32, 33 or 34, 35 in each pair to make only line contact with each other.
  • the two pairs of opposed surfaces 32, 33 and 34. 35 work in combination to guide the main driven plate assembly 1 1 pivotally about the hub 12.
  • This enables the friction linings 15 to rotate about an axis which is not in angular alignment with the axis of rotation of the hub 12 without setting up cyclical stresses in the driven plate 10 and without affecting the operation of either the main torsion damper or the pre-damper 30.
  • the main driven plate assembly 1 1 might be expected to pivot by, for example, 0.25 to 1mm in either direction from the Vertical measured at the outer diameter of the side plates 17, 18 and the central flange 20.
  • the radial clearance between the teeth 21 on the flange 20 and the teeth 14 on the hub 12 enables the main driven plate assembly 1 1 to move radially relative to the hub 12 to a limited extent. Such movement might occur for example when the axis of an associated crankshaft (or flywheel) and the axis of an associated transmission drive shaft are radially offset due to misalignment. This relative radial movement will be resisted by the springs 31 of the pre-damper which will tend to centre the hub 12 relative to the main driven plate assembly 11 in a manner known in the art.
  • the driven plate can compensate for both angular and radial misalignment.
  • Figure 3 shows a modified form of the driven plate of Figures 1 and 2
  • the d ⁇ ven plate m Figure 3 is substantially the same as that shown in Figures 1 and 2 except that the first surfaces 32, 34 are formed directly on the hub 12, whilst the second surfaces 33, 35 are formed on bearing rings 38 and 39 which are located on the radially inner edges of the first and second side plates 17, 18 respectively
  • the side plates 17, 18 can be flat at their radially inner peripheries making them simpler to produce and so reducing manufacturing costs
  • the bearing rings 38, 39 can be made from any suitable material but again are preferably made from a plastics mate ⁇ al having a low co-efficient of friction
  • the bearing rings have a number of slots 41 for engagement by drive lugs 42 on the side plates 17, 18 to ensure that the rings are rotationally fast with the side plates
  • FIG. 4 A further embodiment of a d ⁇ ven plate 1 10 m accordance with the mvention is shown m Figures 4 and 5
  • the d ⁇ ven plate 1 10 is substantially the same as the d ⁇ ven plate 10 of Figures 1 and 2 and features which perform the same function are given the same reference numeral but increased by 100
  • both pairs of opposed surfaces 132, 133 and 134, 135 are arranged on the same axial side of the driven plate
  • One pair of opposed surfaces 132, 133 comprises a first surface 132 on a first bearing ring 136 located on the outer periphery of the hub 1 12 adjacent to the ⁇ ght hand (as viewed in Figure 5) axial side of the teeth 1 14
  • the second surface 133 of this pair is formed on the axially inner surface of a splayed out portion of the radially inner periphery of the first side plate 1 17
  • the other pair of opposed surfaces 134, 135 comprises a first surface 134 provided on a second bearing ring 137 adjacent to the first bearing ring 136 whilst the second surface 135 of this pair is formed on the axiallv outer side of the splayed out portion of the first side plate 1 17
  • the second bearing ring 137 is also located on the outer pe ⁇ pheral surface of the hub 1 12 and has a first portion 137a which
  • one of the pairs of surfaces 132, 133 inhibits movement of the main driven plate assembly 1 11 to the left (as viewed in Figure 5) relative to the hub whilst the other pair of opposed surfaces 134, 135 inhibits movement to the right.
  • the profile of the surface 132 is part-spherical having a centre Z located on the axis of the driven plate whilst the profile of the surface 134 is also part-spherical but is concave whereas the surface 132 is convex.
  • the second surfaces 133, 135 have profiles which conform generally with the profiles of their respective first surfaces 132, 1 4 As with the previous embodiment the opposed surfaces in either pair may have any suitable profile which permits the driven plate main assembly 1 1 1 to tilt relative to the hub 1 12.
  • the first and second bearing rings can be formed of any suitable material but are preferably formed from a plastics material having a low co-efficient of friction.
  • the first bearing ring 136 may have projections 140 which locate in the side of the teeth 1 14 of the hub to ensure that ring 136 rotates with the hub 1 12.
  • the friction washer 126 can be extended radially inwardly to provide an increased area of contact with the second side plate 1 18
  • FIG. 6 A modified version of the friction driven plate 1 10 is shown in Figure 6.
  • This driven plate is identical to the driven plate shown in Figure 5 except that the first portion 137a of the second bearing ring 137 has a reduced axial dimension. This is compensated for by providing an axial extension 136a to the first bearing ring 136. This results in the second bearing ring 137 having a more even cross-section which is easier to manufacture.
  • a further embodiment of a driven plate 210 in accordance with the invention is shown in Figure 7.
  • the driven plate 210 is similar to the driven plate 10 and features which perform the same function are given the same reference numeral but increased by 200.
  • Driven plate 210 has two pairs of opposed surfaces 232, 233 and 234, 235 respectively.
  • the first surfaces 232, 234 of each pair are formed directly on the hub 212.
  • the second surfaces 233, 235 are not mounted on the side plates 217, 218 but are provided on side of the annular flange 220 and are held rotationally fast with each other and the annular flange 220 by means of a number of axially extending arm portions 245 on plate 244 which extend the through corresponding openings in the annular flange 20 and 243.
  • the arm portions 245 may be arranged so as to clip on to the intermediate plate 243 so holding the intermediate plates 243, 244 and the annular flange 20 together to form a sub-assembly for manufacturing purposes.
  • the plates 243, 244 have windows or recess 246 which align with damping springs 23 1 a ⁇ anged between consecutive teeth 214 on the hub 212.
  • the windows or recess 246 engage with the ends of the springs so that relative rotational movement between the intermediate plates 243, 244 and the hub 212 results in the springs being compressed between the recesses 246 and the teeth 214 of the hub in a manner well known in the art.
  • the Driven plate 210 has two friction dampers 225, 247 which provide hysteresis damping for the main torsion damper and the pre-damper respectively
  • the first friction damper 225 comprises a friction washer 248 having a radially extending portion 248a which is in contact with the axially outer face of the intermediate plate 243, and a number of axially extending lugs 248b which engage in corresponding openings 217a in the side plate 217
  • a spring washer 229 acts between the friction washer 248 and the side plate 217 clamping the radially extending portion 248a against the intermediate plate 243 and also clamping intermediate plate 244 against the second side plate 218.
  • the second friction damper 247 comprises a radially extending friction washer 249 which contacts the axially inner surface of the first side plate 217.
  • the friction washer 249 has a number of radially inwardly directed drive formations 249a which engage with splines 250 formed on the outer periphery of the hub 212 so that the friction washer 249 is rotationally fast with the hub.
  • a spring washer 251 acts between the intermediate plate 243 and the friction washer 249 to bias the friction washer into contact with the side plate 217. Relative rotational movement between the hub and side plate 217 results in relative movement between the friction washer 249 and the side plate 217 generating a friction damping force operative over the complete range of movement of both the pre-damper and the main torsion damper.
  • the spring force of the spring washer 251 is small in comparison with the spring force of the spring washer 229 so that the damping force generated by the damper 247 is small compared to the 1 friction damping force generated by the damper 225. It should also be noted that the spring force of the spring washer 251 is not sufficient to cause an axial loading to be generated between the opposed surfaces 232, 233. Since neither of the friction dampers 225, 247 results in axial loading of the two pairs of opposed surface 232, 233 and 234, 235 the friction forces between the opposed surfaces are kept to a minimum.
  • the intermediate plates 243, 244 can be made of any suitable material but preferably are made from a plastics material.
  • first surfaces 232, 234 could be provided on separate bearing rings mounted about the periphery of the hub 212.
  • Such bearing rings may be rotationally fixed to the hub by having drive formations for engagement with splines formed on the periphery of the hub.
  • FIG 8 shows driven plate 3 10 which is a modified version of the driven plate 210 and features of plate 310 which perform the same function of those of plate 210 are given the same reference numeral but increased by 100.
  • the first surface 332 is formed on a bearing ring 336 which is mounted about the outer periphery of the hub 3 12.
  • the bearing ring 336 has a number of radially inwardly directed drive formations 336a which engage with splines 350 formed on the outer periphery of the hub 312 so that the bearing ring 336 rotates with the hub 312.
  • the second surface 333 which opposes the first surface 332, is provided on a modified friction washer 349 of the friction damper 347.
  • the modified friction washer 349 is generally L-shaped having a radially extending portion 349a biased into contact with the axially inner face of the first side plate 317 by spring washer 351 and an axially extending portion 349b which lies adjacent the radially inner end of the side plate 317.
  • the surface 333 is formed at the junction of the radially 349a and axially 349b extending portions of the friction washer 349 facing the surface 332 on the bearing ring 336.
  • a number of drive lugs 333a project from the surface 333 for engagement with corresponding grooves 332a in the surface 332. This ensures that the friction washer 349 rotates with the bearing ring 336 which in turn is constrained to rotate with the hub 312 as described above.
  • the arrangement is such that relative rotational movement between the hub 312 and the side plate 3 17 results in relative movement between the radially extending portion 349a of the friction washer 349 and the side plate 317 to generate a friction damping force.
  • the spring washer 351 acts between the intermediate plate 343 and the radially extending portion 349a of the friction washer 349 and so does not produce an axial loading between the surfaces 332, 333.
  • Driven plate 310 has the advantage that by arranging the second surface 333 on the modified friction washer 249, it is possible for the pairs of opposed surfaces to be spaced further apart axially This provides a greater degree of control over the tilting movement of the main driven plate assembly relative to the hub.
  • the invention is not limited to application in driven plates according to the preferred embodiments but can be applied to any driven plate of the type described.
  • the preferred embodiments relate to driven plates having torsional dampers
  • the invention can equally be applied to so called rigid driven plates in which no torsional damper is provided or to driven plates of the type described which have only an idle damper for isolating the drive line from low level vibrations

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

L'invention concerne un disque d'embrayage (10) comprenant un ensemble principal (11) connecté par entraînement à un moyeu (12) à l'aide de formations (14, 21) de commande assemblées l'une dans l'autre avec un jeu radial et circonférentiel limités permettant à l'ensemble principal de se déplacer de manière radiale et circonférentielle par rapport au moyeu de façon limitée. Le disque d'embrayage comprend également deux paires de surfaces opposées (32, 33; 34, 35), chaque paire de surfaces opposées comprenant une première surface (32, 34) associée au moyeu (12) et une seconde surface (33, 35) associée à l'ensemble principal du disque d'embrayage. Au moins une des surfaces dans chaque paire est inclinée de manière oblique par rapport à l'axe de rotation du disque d'embrayage, une des paires de surfaces opposées étant destinée à inhiber le mouvement de l'ensemble principal du disque d'embrayage par rapport au moyeu dans une première direction axiale du disque d'embrayage, et l'autre paire étant destinée à inhiber le mouvement de l'ensemble principal du disque d'embrayage par rapport au moyeu dans la direction axiale opposée du disque d'embrayage. Cette configuration permet à l'ensemble principal (11) du disque d'embrayage d'être incliné par rapport à l'axe du moyeu central (12), la première et la seconde surface de chaque paire coulissant l'une par rapport à l'autre.
EP01949747A 2000-07-21 2001-07-18 Disques d'embrayage pour embrayages a friction Withdrawn EP1216365A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB0017798A GB0017798D0 (en) 2000-07-21 2000-07-21 Driven plates for friction clutches
GB0017798 2000-07-21
PCT/GB2001/003230 WO2002008635A1 (fr) 2000-07-21 2001-07-18 Disques d'embrayage pour embrayages a friction

Publications (1)

Publication Number Publication Date
EP1216365A1 true EP1216365A1 (fr) 2002-06-26

Family

ID=9896008

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01949747A Withdrawn EP1216365A1 (fr) 2000-07-21 2001-07-18 Disques d'embrayage pour embrayages a friction

Country Status (5)

Country Link
EP (1) EP1216365A1 (fr)
JP (1) JP2004504571A (fr)
AU (1) AU2001270864A1 (fr)
GB (2) GB0017798D0 (fr)
WO (1) WO2002008635A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016214686A1 (de) * 2016-08-08 2018-02-08 Zf Friedrichshafen Ag Kopplungsanordnung
JP7299828B2 (ja) * 2019-12-09 2023-06-28 株式会社エクセディ ダンパ装置
JP7376334B2 (ja) * 2019-12-09 2023-11-08 株式会社エクセディ ダンパ装置
JP7384654B2 (ja) * 2019-12-09 2023-11-21 株式会社エクセディ ダンパ装置

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3248119A1 (de) * 1982-12-24 1984-06-28 LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl Kupplungsscheibe
DE3743075A1 (de) * 1987-12-18 1989-06-29 Fichtel & Sachs Ag Torsionsschwingungsdaempfer mit waelzlagerung
DE19545973C1 (de) * 1995-12-09 1997-06-12 Fichtel & Sachs Ag Kupplungsscheibe mit Zentriereinrichtung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0208635A1 *

Also Published As

Publication number Publication date
JP2004504571A (ja) 2004-02-12
AU2001270864A1 (en) 2002-02-05
WO2002008635A1 (fr) 2002-01-31
GB0017798D0 (en) 2000-09-06
GB0205319D0 (en) 2002-04-17
GB2372299A (en) 2002-08-21
GB2372299B (en) 2004-09-29

Similar Documents

Publication Publication Date Title
US4638684A (en) Assembly for taking up and compensating for torque-induced shocks
US4684007A (en) Clutch plate
US5139124A (en) Apparatus for compensating for fluctuations of torque between the engine and the transmission of a motor vehicle
US6119839A (en) Torsional vibration damper
US4751992A (en) Composite flywheel with slip clutch
US7766142B2 (en) Torque transmission device
US6209419B1 (en) Twin mass flywheel friction damping device
US4760754A (en) Apparatus for transmitting torque between flywheels in the power train between the engine and the transmission of a motor vehicle
JP2550040B2 (ja) 内燃機関の回転衝撃を補償する装置
US7467699B2 (en) Double mass flywheel
US20020153221A1 (en) Friction clutch
GB2329230A (en) Torsional vibration damper having couplings rolling in sprung recesses.
GB1586498A (en) Torsional vibration damper
EP0790433B1 (fr) Elément de plaque pour un ensemble de disque amortisseur comportant des pièces de support s'étendant radialement
WO1998044276A2 (fr) Amortisseur de vibrations torsionnelles
US4526261A (en) Clutch plate with control means and at least two energy storing devices cooperating with the control means
WO2002008635A1 (fr) Disques d'embrayage pour embrayages a friction
US6719112B2 (en) Torsion damping mechanism with auxiliary mass
GB2337573A (en) Clutch disc with hub centring spring
EP1427947B1 (fr) Disque d'embrayage
EP1227257A2 (fr) Disques d'embrayage pour embrayages à friction
US20040206201A1 (en) Flywheel assembly
KR100602312B1 (ko) 자동차용 마찰 클러치의 토션 댐퍼
KR100602305B1 (ko) 마찰 클러치 디스크용 비틀림 댐퍼
GB2209577A (en) Torsional damper

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20020321

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RBV Designated contracting states (corrected)

Designated state(s): DE FR GB IT

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20040922