GB2150654A - Friction disc clutch - Google Patents

Friction disc clutch Download PDF

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Publication number
GB2150654A
GB2150654A GB08429499A GB8429499A GB2150654A GB 2150654 A GB2150654 A GB 2150654A GB 08429499 A GB08429499 A GB 08429499A GB 8429499 A GB8429499 A GB 8429499A GB 2150654 A GB2150654 A GB 2150654A
Authority
GB
United Kingdom
Prior art keywords
friction
disc
friction plate
clutch
clutch according
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.)
Granted
Application number
GB08429499A
Other versions
GB8429499D0 (en
GB2150654B (en
Inventor
Dieter Lutz
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.)
Sachs Systemtechnik GmbH
Original Assignee
Sachs Systemtechnik GmbH
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 Sachs Systemtechnik GmbH filed Critical Sachs Systemtechnik GmbH
Publication of GB8429499D0 publication Critical patent/GB8429499D0/en
Publication of GB2150654A publication Critical patent/GB2150654A/en
Application granted granted Critical
Publication of GB2150654B publication Critical patent/GB2150654B/en
Expired 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
    • F16F15/131—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 the rotating system comprising two or more gyratory masses
    • F16F15/13142—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 the rotating system comprising two or more gyratory masses characterised by the method of assembly, production or treatment
    • F16F15/1315—Multi-part primary or secondary masses, e.g. assembled from pieces of sheet steel
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
    • F16D13/71—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members in which the clutching pressure is produced by springs only
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
    • F16D2013/706—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members the axially movable pressure plate is supported by leaf springs

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

The fly-wheel (1) of the motor vehicle friction disc clutch and/or its presser plate (13) consists of a lighter material than in conventional clutches, for example of carbon- fibre-reinforced thermosetting synthetic plastics material or aluminium. To increase the moment of inertia of the clutch, heavy material particles (37) for example of cast iron, steel or a heavy mineral are incorporated into the radially outer region of the fly-wheel (1) and/or of the pressure plate (13). A radially ribbed sheet metal securing disc (3) stiffens the clutch axially and in the circumferential direction. The clutch cover (11) initially stresses the fly-wheel (1) radially in order better to be able to take up centrifugal forces. The flywheel may carry a friction lining (35) of carbon-fibre-reinforced carbon or of aluminium to improve its friction properties. <IMAGE>

Description

SPECIFICATION Friction disc clutch The invention relates to a friction disc clutch, especially for a motor vehicle, comprising a first friction plate drivable about an axis of rotation, a second friction plate guided fast in rotation but axially displaceably on the first friction plate, a clutch disc coaxially arranged axially between the first friction plate and the second friction plate and rotatable in relation to the friction plates, a spring device axially resiliently initially stressing the second friction plate towards the first friction plate, and a releaser device.
In conventional friction disc clutches of the above-stated kind the first friction plate is formed as fly-wheel and consists of a onepiece, relatively heavy, steel disc with predetermined moment of inertia.
It is the problem of the invention to indicate a way in which the total weight of the clutch can be reduced for a predetermined moment of inertia.
In accordance with the invention this problem is solved in that at least one of the two friction plates consists in its radially outer region of a material the specific weight of which is higher than the specific weight of its radially inner region. The radially inner regions, especially of the friction plate which forms the fly-wheel, contribute only little to the moment of inertia but increase the weight.
The weight of the clutch can be reduced considerably if the radially outer regions of the clutch, which contribute comparatively greatly to the moment of inertia, alone are produced from a heavy material, while the radially inner regions of the friction plate, which contribute only comparatively little to the moment of inertia, are produced from a light material.
The weight reduction can be achieved in that the friction plate as a whole consists of a light material and carries a ring of heavy material on its circumference. By way of example synthetic plastics material, especially carbon-fibre-reinforced thermosetting plastics material, or aluminium can be used as light material. In place of adding the heavier material as a homogeneous ring on to a disc or annular disc of the ligher material, it is possible to increase the specific weight of the synthetic plastics material or aluminium locally by incorporation of particles of the heavier material. Cast iron, steel or equally relatively heavy minerals, such for example as barium sulphate or the like, are suitable as heavy material particles.If the friction properties of the materials used for the friction plates do not conform with requirements, the friction plates can be lined with additional friction linings, especially of carbon-fibre-reinforced carbon.
In a preferred form of embodiment a ring consisting preferably of steel is drawn with press fit on to the external circumference of the friction plate which forms the fly-wheel.
The ring, which can be utilised at the same time as clutch cover, takes up occurring centrifugal forces. The ring is rolled in along its edge axially remote from the other friction plate, forming a radially inwardly extending annular flange grasping behind the first friction plate. Due to the rolling-in the ring is not only axially secured but also braced with radial initial stress firmly on to the external circumference of the friction plate.
For the securing of the friction plate which forms the fly-wheel a sheet metal disc provided with corrugations is preferably provided.
The corrugations stiffen the sheet metal disc both axially and in the circumferential direction. The sheet metal disc transmits the torque from the crank-shaft to the friction plates and takes up the axial disengagement force of the clutch. The external diameter of the sheet metal disc is expediently equal to or greater than the external diameter of the clutch disc and it extends into the securing region of the clutch cover.
The corrugations preferably run substantially radially dfthe rotation axis and form cooling air passages between the sheet metal disc and the adjacent friction plate.
The invention is to be explained in greater detail below by reference to drawings wherein:- Figure 1 shows an axial longitudinal section through the upper half of a pulled-type motor vehicle friction disc clutch; Figure 2 shows a radial detail view of the clutch according to Fig. 1, seen in the direction II; Figure 3 shows an axial longitudinal section through the upper half of a pressed-type motor vehicle friction disc clutch and Figure 4 shows an axial longitudinal section through the upper half of another form of embodiment of a pulled-type motor vehicle friction disc clutch.
The pulled-type motor vehicle friction disc clutch as illustrated in Figs. 1 and 2 comprises a fly-wheel 1 which is coaxially secured by means of an annular sheet metal disc 3 on a flange 5 of a crank-shaft 9 rotating about an axis 7 of rotation. The fly-wheel 1 carries a substantially annular clutch cover 11 which, on the side of the fly-heel 1 axially remote from the crank-shaft 9 encloses a presser plate 1 3 of substantially annular disc form.
The presser plate 1 3 is guided fast in rotation but axially displaceably on the clutch cover 11 with the aid of several tangential straps 1 5 arranged in distribution in the circumferential direction. A clutch disc 17, which is coupled in the usual way axially displaceably but fast in rotation with an input shaft 1 9 of a gear (not shown further), is arranged axially between the fly-wheel 1 and the presser plate 13, coaxially with the rotation axis 7. The clutch disc 1 7 carries friction linings 21 and can comprise torsional vibration dampers indicated at 23 and frictional vibration dampers (not illustrated further).A diaphragm spring 25, which resiliently initially stresses the presser plate 1 3 through the friction linings 21 of the clutch disc 1 7 against the fly-wheel 1, is clamped in between the clutch cover 11 for the one part and the presser plate 1 3 for the other.In this case the diaphragm spring 25 is supported in the region of its external circumference on the clutch cover 11 and iies, along a diameter between the external diameter and the internal diameter, against projections 27 of the presser plate 1 3. The presser plate 1 3 can be relieved of the pressure-application force of the diaphragm spring 25, and the clutch can be disengaged, by means of a release anti-friction bearing 31 which is axially displaceably guided on a guide tube of the gear and acts on the radially inner ends of the tongues of the diaphragm spring 25.
The fly-wheel 1 consists of a material which is lighter than conventional fly-wheel materials, especially of carbon-fibre-reinforced thermosetting synthetic plastics material, for example phenol resin or epoxy resin. Into the radially outer region of the fly-wheel, which supplies a comparatively high contribution to the moment of inertia, there are incorporated particles 33 of heavy substance which increase the specific weight of the synthetic plastics material in the radially outer region in comparison with the radially inner region, which is free from particles of heavy material.
The heavy material particles can consist for example of cast iron, steel or a heavy mineral, for example barium sulphate. The presser plate 13, which preferably likewise consists of a material lighter than conventional presser plates, is preferably produced from the material of the fly-wheel. Here again, as indicated at 34, particles of heavy material of the kind as stated above can be incorporated to increase the inertia moment in the radially outer region.
The fly-wheel 1 carries a friction lining 35 to improve the friction properties. The friction lining can consist for example of carbon-fibrereinforced carbon or aluminium, and may be omitted. Alternatively the presser plate 1 3 too may be provided with such a friction lining.
The clutch cover 11 surrounds a radially protruding annular flange 37 of the fly-wheel 1. It is seated with radial initial stress with press fit on the external circumference of the annular flange 37 and takes up the centrifugal forces acting upon the material of the flywheel. The edge of the clutch cover 11 axially remote from the diaphragm spring 25 is rolled in behind the end face on the crank-shaft side of the fly-wheel 1 and forms a radially inwardly extending annular flange 39 which holds the clutch cover 11 on the fly-wheel 1.
By the rolling-in of the edge of the clutch cover 11 at the same time the clutch cover 11 is radially clamped firmly on to the flywheel 1. In the opposite axial direction a shoulder 41 facing axially towards the annular flange 39 fixes the clutch cover 11 on the flywheel 1. On the outer side of the channel formed by the shoulder 41 there is seated a toothed ring 43 for the engagement of the starter pinion.
The sheet metal disc 3 is screwed at its radially inner edge with screws 45 to the flange 5 of the crank-shaft 9. The sheet metal disc 3 protrudes radially inwards beyond the internal circumference of the fly-wheel 1 of substantially annular disc form and extends radially outwards substantially to the external circumference of the fly-wheel 1, where it is screwed with screws 47 through the annular flange 39 to the fly-wheel 1. Into the sheet metal disc 3 there are pressed substantially radially extending ribs or corrugations 49 which stiffen the sheet metal disc both axially and in the circumferential direction. The corrugations extending between the sheet metal disc 3 and the fly-wheel 1 form cooling air passages open radially on both sides of the fly-wheel 1 for the cooling of the fly-wheel 1.
Between successive cooling air passages in the circumferential direction the fly-wheel can bear over its entire radial width on the sheet metal disc 3.
The fly-wheel 1, the presser plate 13, the clutch disc 1 7 and the diaphragm spring 25 form one unit which can be secured as such by means of the screws 47 detachably to the sheet metal disc 3 and thus to the crank-shaft 9. Such a construction unit can be fitted more easily than conventional clutches where the pressure plate unit must be secured against the force of the diaphragm spring to the flywheel. If desired additional centring journals or the like to facilitate centring may be provided.
Fig. 3 shows a pressed-type motor vehicle friction disc clutch which differs from the clutch according to Figs. 1 and 2 essentially only in the arrangement of its tangential straps guiding the presser plate on the flywheel and in the supporting, differing according to the type of actuation, of the diaphragm spring on the clutch cover, the presser plate and the releaser anti-friction bearing. Parts of like action are designated by reference numerals increased by the figure 100 compared with Figs. 1 and 2. For more detailed explanation to this extent reference is made to the description of Figs. 1 and 2.
In detail, the noses 1 27 of the presser plate 11 3 are arranged on its external circumference and are supported on the diaphragm spring 1 25 in the region of its external circumference. The clutch cover 111 extends on the side axially remote from the presser plate 11 3 into a middle region of the diaphragm spring 125, which in this region is supported on the clutch cover 111. The presser plate 11 3 is relieved of the initial stress force of the diaphragm spring 125 by a release movement of the releaser anti-friction bearing 1 31 directed towards the crank-shaft 109.The tangential straps 11 5 are secured with their one end on the presser plate 113, but with their other end directly, that is not through the cover 111, on the fly-wheel 101. This style of securing facilitates the assembly of the clutch and may also be used in the case of the pulley-type clutch according to Fig. 1. More especially the manner of the weight distribution of the fly-wheel 101 and possibly of the presser plate 11 3 if appropriate is dimensioned in conformity with the drawn-type clutch in Figs. 1 and 2. Likewise the securing of the clutch construction unit on the sheet metal disc 103 is selected in the same way.
Fig. 4 shows a drawn-type motor vehicle friction disc clutch the fly-wheel 201 of which is secured directly by means of screws 203 to a flange 205 of a crank-shaft 209 which rotates about the rotation axis 207. The clutch comprises a cover 211 which is screwed by means of screws 21 2 to the axial end face of the fly-wheel 201 remote from the crankshaft. The cover 211 encloses a presser plate 21 3 which is secured fast in rotation but axially displaceably on the housing 211 by means of a plurality of tangential straps 21 5 distributed in the circumferential direction.Axially between the presser plate 21 3 and the fly-wheel 201 there is arranged a clutch disc 217 which is seated in the usual way fast in rotation but axially displaceably on an input shaft 21 9 of the gear (not shown further). The clutch disc 21 7 carries friction linings 221 and may comprise a torsional vibration damper 223. A diaphragm spring 225 is supported in the region of its external circumference on the clutch cover 211 and lies, on a circle between its external circumference and its internal circumference, upon noses 227 of the presser plate 213. The presser plate 213 can be relieved of load and the clutch disengaged by means of a releaser 229.
The fly-wheel 201 is of substantially annular disc form and in the region of the friction linings 221 of the clutch disc 217 likewise carries a friction lining 231 of carbon-fibrereinforced carbon or aluminium. Moreover the fly-wheel 201 consists of a lighter material than conventional fly-wheels, for example of carbon-fibre-reinforced thermosetting synthetic plastics material or aluminium, and particles 233 of heavy substance are incorporated in the radially outer region of the flywheel to increase the moment of inertia. The heavy substance particles can again consist of cast iron, steel or a mineral, for example barium sulphate. The external circumference of the fly-wheel 201 can contain additional reinforcing layers 235 in order better to be able to take up centrifugal forces.
The clutch according to Fig. 4 can also be constructed as a pressed-type clutch.

Claims (14)

1. Friction disc clutch, especially for a motor vehicle, comprising a) a first friction plate (1; 101; 201) drivable about a rotation axis, b) a second friction plate (13; 113; 213) guided fast in rotation but axially displaceably on the first friction plate 101; 201).
c) a clutch disc (17; 117; 217) coaxially arranged axially between the first friction plate (1; 101; 201) and the second friction plate (13; 113; 213) and rotatable in relation to the friction plates, d) a spring device (25; 125; 225) which initially stresses the second friction plate (13; 113; 213) axially resiliently towards the first friction plate (1; 101;201)and e) a releaser device (31; 131; 229), characterised in that at least one of the two friction plates (1; 101; 201) consists in its radially outer region of a material the specific weight of which is greater than the specific weight of its radially inner region.
2. Friction disc clutch according to Claim 1, characterised in that at least one of the two friction plates (1; 101; 2p1) is produced from a first material into which, in the outer region of the friction plate, there are incorporated particles of a second material with higher specific weight than the first material.
3. Friction disc clutch according to Claim 2, characterised in that the first material is synthetic plastics material or light metal.
4. Friction disc clutch according to Claim 3, characterised in that the first material is a carbon-fibre-reinforced thermosetting synthetic plastics material.
5. Friction disc clutch according to one of Claims 2 to 4, characterised in that the second material is cast iron, steel, heavy metal or a mineral.
6. Friction disc clutch according to one of Claims 1 to 6, characterised in that at least one of the two friction plates (1; 101; 201) carries a friction lining (35; 135; 231) against which the clutch disc (17; 117; 217) rests with its friction linings (21; 121; 221).
7. Friction disc clutch according to Claim 6, characterised in that the friction lining (35; 135; 231) of the friction plate (1; 101; 201) consists of carbon-fibre-reinforced carbon or light metal.
8. Friction disc clutch according to one of the preceding Claims, characterised in that the first friction plate (1; 101; 201) has a higher specific weight in its radially outer region than in its inner region and in that a closed ring (11; 111; 235) firmly encloses the external circumference of the first friction plate (1; 101; 201).
9. Friction disc clutch according to Claim 8, characterised in that the ring is formed as an annular clutch cover (11; 111) on which there is supported a spring (25; 125) of disc form supported on the second friction plate (13; 113).
10. Friction disc clutch according to Claim 8 or 9, characterised in tat the ring (11; 111) is rolled in along its edge axially remote from the second friction plate (13; 11 3) forming a radially inwardly extending annular flange (39; 139) which grasps behind the first friction plate (1; 101).
11. Friction disc clutch according to one of Claims 1 to 9, characterised in that the first friction plate (1; 101) has the form of an annular disc and carries a sheet metal disc (3; 103) protruding radially inwards beyond the inner edge of the annular disc, into which sheet metal disc there are pressed corrugations (49; 149) which stiffen the sheet metal disc (3; 103) both axially and in the circumferential direction.
1 2. Friction disc clutch according to Claim 11, characterised in that the external diameter of the sheet metal disc (3; 103) is equal to or greater than the external diameter of the clutch disc (17; 117).
1 3. Friction disc clutch according to Claim 11 or 12, characterised in that the corrugations (49;) 149) proceed substantially radially and form radial cooling air passages axially between the sheet metal disc (3; 103) and the annular disc (1; 101).
14. Friction disc clutcb according to one of Claims 1 to 13, in which the second friction plate (113) is held fast in rotation but axially displaceably on the first friction plate (101) through several tangential straps (115) distributed in the circumferential direction, characterised in that the ends of the tangential straps (11 5) are secured directly on the first friction plate (101) for the one part and the second friction plate (113) for the other part.
1 5. A friction clutch substantially as described with reference to Figs. 1 and 2, Fig. 3 or Fig. 4 of the accompanying drawings.
GB08429499A 1983-12-01 1984-11-22 Friction disc clutch Expired GB2150654B (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19833343505 DE3343505A1 (en) 1983-12-01 1983-12-01 FRICTION DISC COUPLING

Publications (3)

Publication Number Publication Date
GB8429499D0 GB8429499D0 (en) 1985-01-03
GB2150654A true GB2150654A (en) 1985-07-03
GB2150654B GB2150654B (en) 1987-02-04

Family

ID=6215785

Family Applications (1)

Application Number Title Priority Date Filing Date
GB08429499A Expired GB2150654B (en) 1983-12-01 1984-11-22 Friction disc clutch

Country Status (3)

Country Link
DE (1) DE3343505A1 (en)
FR (1) FR2556062A1 (en)
GB (1) GB2150654B (en)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1992008063A1 (en) * 1990-11-02 1992-05-14 Automotive Products Plc Friction clutch cover assemblies
FR2678332A1 (en) * 1991-06-27 1992-12-31 Valeo CLUTCH WITH END OF SHAFT, IN PARTICULAR FOR MOTOR VEHICLE.
EP0548871A1 (en) * 1991-12-23 1993-06-30 Chrysler Corporation Vehicle modular clutch attaching arrangement
GB2265193A (en) * 1990-11-02 1993-09-22 Automotive Products Plc Friction clutch cover assemblies
FR2723772A1 (en) * 1994-08-17 1996-02-23 Fichtel & Sachs Ag MODULAR MOUNT FLYWHEEL DEVICE
FR2812694A1 (en) * 2000-08-07 2002-02-08 Mannesmann Sachs Ag FRICTION CLUTCH
EP1350976A1 (en) * 2002-04-02 2003-10-08 Sachs Giesserei GmbH Friction clutch
US6793057B1 (en) * 2002-12-31 2004-09-21 Robert P. Smith, Jr. Rotary friction system
WO2018072779A1 (en) * 2016-10-21 2018-04-26 Schaeffler Technologies AG & Co. KG Torsional vibration damper

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2224789A (en) * 1988-11-11 1990-05-16 Fichtel & Sachs Ag Friction clutch
DE3916853C2 (en) * 1988-11-11 1997-10-02 Fichtel & Sachs Ag Friction clutch with separate bearing of the clutch disc
KR100588342B1 (en) * 2003-11-26 2006-06-12 주식회사 데크 Clutch for transmission power
US20170108054A1 (en) 2014-03-27 2017-04-20 Schaeffler Technologies AG & Co. KG Sheet metal pressure plate and pressure pot as joint component
DE102015204998A1 (en) * 2015-03-19 2016-09-22 Schaeffler Technologies AG & Co. KG Coupling with pressure plate segment holding support structure
FR3127793A1 (en) * 2021-10-05 2023-04-07 Valeo Embrayages FLYWHEEL ASSEMBLED WITH DUAL MATERIALS

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE676453C (en) * 1937-11-25 1939-06-03 Continental Gummi Werke Akt Ge Torsional vibration damper
DE705717C (en) * 1939-03-07 1941-05-08 Continental Gummi Werke Akt Ge Torsional vibration damper for the crankshaft of internal combustion engines
DE2853298A1 (en) * 1978-12-09 1980-06-19 Klaue Hermann Clutch-flywheel assembly for vehicle - has light alloy rings for friction pads to improve heat dissipation
DE2923887A1 (en) * 1979-06-13 1980-12-18 Alusuisse FRICTION CLUTCH WITH CLUTCH DISC AND METHOD FOR THE PRODUCTION THEREOF
DE2949125A1 (en) * 1979-12-06 1981-06-11 Daimler-Benz Ag, 7000 Stuttgart Energy storage flywheel for vehicle installation - has high-density fibre-reinforced wheel rim to increase rotational speed
FR2474587B1 (en) * 1979-12-18 1988-06-03 Laverlochere Jacques FLYWHEEL FOR EXPLOSION ENGINES WITH DIFFERENT DENSITY COMPONENTS
FR2506672A1 (en) * 1981-06-02 1982-12-03 Lorraine Carbone METHOD FOR MANUFACTURING FRICTION DISCS
FR2526102B1 (en) * 1982-04-29 1985-08-09 Valeo CLUTCH WITH TWO-PART REACTION PLATE, ESPECIALLY FOR A MOTOR VEHICLE
FR2526105A1 (en) * 1982-04-29 1983-11-04 Valeo CLUTCH, PARTICULARLY FOR MOTOR VEHICLES, WITH IMPROVED ASSEMBLY OF THE COVER ON THE REACTION TRAY
FR2525934B1 (en) * 1982-04-29 1985-08-09 Valeo METHOD FOR MANUFACTURING AND MOUNTING HOLLOW BODIES SUCH AS A COVER AND IGNITION TARGET OF A CLUTCH MECHANISM

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1992008063A1 (en) * 1990-11-02 1992-05-14 Automotive Products Plc Friction clutch cover assemblies
GB2265193A (en) * 1990-11-02 1993-09-22 Automotive Products Plc Friction clutch cover assemblies
GB2265193B (en) * 1990-11-02 1995-02-22 Automotive Products Plc Friction clutch cover assemblies
FR2678332A1 (en) * 1991-06-27 1992-12-31 Valeo CLUTCH WITH END OF SHAFT, IN PARTICULAR FOR MOTOR VEHICLE.
EP0548871A1 (en) * 1991-12-23 1993-06-30 Chrysler Corporation Vehicle modular clutch attaching arrangement
FR2723772A1 (en) * 1994-08-17 1996-02-23 Fichtel & Sachs Ag MODULAR MOUNT FLYWHEEL DEVICE
ES2125760A1 (en) * 1994-08-17 1999-03-01 Fichtel & Sachs Ag Friction clutch for the transmission of a motor vehicle and a flywheel assembly for a friction clutch
FR2812694A1 (en) * 2000-08-07 2002-02-08 Mannesmann Sachs Ag FRICTION CLUTCH
EP1350976A1 (en) * 2002-04-02 2003-10-08 Sachs Giesserei GmbH Friction clutch
US6905010B2 (en) 2002-04-02 2005-06-14 Zf Sachs Ag Friction clutch assembly
US6793057B1 (en) * 2002-12-31 2004-09-21 Robert P. Smith, Jr. Rotary friction system
WO2018072779A1 (en) * 2016-10-21 2018-04-26 Schaeffler Technologies AG & Co. KG Torsional vibration damper

Also Published As

Publication number Publication date
GB8429499D0 (en) 1985-01-03
FR2556062A1 (en) 1985-06-07
DE3343505C2 (en) 1993-05-06
GB2150654B (en) 1987-02-04
DE3343505A1 (en) 1985-06-13

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