GB2176256A - Thrust plate unit for friction clutch - Google Patents
Thrust plate unit for friction clutch Download PDFInfo
- Publication number
- GB2176256A GB2176256A GB08611610A GB8611610A GB2176256A GB 2176256 A GB2176256 A GB 2176256A GB 08611610 A GB08611610 A GB 08611610A GB 8611610 A GB8611610 A GB 8611610A GB 2176256 A GB2176256 A GB 2176256A
- Authority
- GB
- United Kingdom
- Prior art keywords
- thrust
- abutment ring
- presser plate
- clutch
- plate unit
- 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- Withdrawn
Links
- 238000013459 approach Methods 0.000 claims description 3
- 230000002441 reversible effect Effects 0.000 abstract description 2
- 210000000887 face Anatomy 0.000 description 14
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 210000001331 nose Anatomy 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/75—Features relating to adjustment, e.g. slack adjusters
- F16D13/757—Features relating to adjustment, e.g. slack adjusters the adjusting device being located on or inside the clutch cover, e.g. acting on the diaphragm or on the pressure plate
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- 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)
- Mechanical Operated Clutches (AREA)
Abstract
A thrust plate unit for a motor vehicle friction clutch comprises an abutment ring (17) having a knife edge (19) and guided axially in a pressure plate (11) while supported by a plurality of wedges (53) on the pressure plate (11). The support takes place through oblique faces (49) (51) in a non-reversible manner, the wedges being displaced automatically either by centrifugal force, as shown, or by spring force (Figs. 3-5) in order to compensate for wear-caused deviations of position between the pressure plate (11) and a diaphragm spring (15) of the clutch. The thrust plate unit further includes a device (27) which also compensates for wear and is automatically adjusted to limit the maximum stroke of the pressure plate (11) with respect to the cover (7). <IMAGE>
Description
SPECIFICATION
Thrust plate unit for a motor vehicle friction clutch
The invention relates to a thrust plate unit for a motor vehicle friction clutch.
The friction linings of motor vehicle friction clutches wear away in operation, whereby the position of the presser plate which presses the clutch disc against the fly-wheel changes.
According to the variation of position of the presser plate, the position of the diaphragm spring and the position of the release elements of the clutch must also be readjusted.
An automatic readjustment device for the presser plate of a motor vehicle friction clutch is known from Fed. German Patent No.
2,920,932. The readjustment device comprises an abutment ring guided axially movably on the presser plate and supported on the presser plate through oblique axial thrust faces rising in the circumferential direction of the ring. The diaphragm spring in turn is supported through the abutment ring on the presser plate. Variations of position of the presser plate in relation to the diaphragm spring can be compensated by rotation of the abutment ring in relation to the presser plate. Tension springs acting in the circumferential direction exert upon the abutment ring a displacement force by which the abutment ring is initially stressed through the oblique axial thrust faces towards the diaphragm spring. A ratchet device prevents the abutment ring from setting itself back again on loading by the diaphragm spring.The known adjustment device further comprises a self-adjusting stroke-limiter device which limits the lift-off stroke of the presser plate to a predetermined play, irrespective of the wear-determined position of the presser plate.
It is the problem of the invention to simplify a thrust plate unit in which devices are provided for the automatic compensation of wear-caused variations of position of the presser plate.
In the thrust plate unit in accordance with the invention the diaphragm spring is supported through an abutment ring on the presser plate, which abutment ring is axially movably guided on the presser plate. The abutment ring for its part is supported on the presser plate through several thrust bodies arranged in distribution in the circumferential direction. The thrust bodies have abutment faces lying substantially axially opposite to one another on which there rest associated abutment faces of the presser plate for one part and of the abutment ring for the other part. At least two of these abutment faces extend obliquely to one another at an angle effecting non-reversibility.
The use of thrust bodies simplifies the production of the oblique faces. Additional devices to prevent reverse rotation of the abutment ring under loading by the diaphragm spring become superfluous due to the nonreversibility.
In a first development of the invention the thrust bodies are formed as wedges which are movable radially in relation to the axis of rotation of the clutch. The wedges expediently taper from the clutch rotation axis radially outwards and are displaced by centrifugal forces in the operation ofthe clutch, for the adjustment movement. The wedges can additionally be used to connect the abutment ring fast in rotation with the presser plate, so that the abutment ring is held in constant angular position in relation to the diaphragm spring, which reduces abrasion damage to its knife edge.
In a second development the abutment ring is seated in an annular groove of the presser plate. The thrust bodies are formed as balls which are fixed in pockets of the annular groove, in the circumferential direction of the groove. Compression springs which initially stress the abutment ring resiliently in the circumferential direction for the movement along its oblique faces are supported on the balls for one part and on shoulders of the abutment ring for the other part. In this development a comparatively simple assembly results.
Examples of embodiment of the invention are to be explained in greater detail below by reference to drawings, wherein:
Figure 1 shows a partial axial longitudinal section through a motor vehicle friction clutch;
Figure 2 shows a detail of a variant of the clutch according to Fig. 1;
Figure 3 shows a partial axial longitudinal section through another form of embodiment of a motor vehicle friction clutch;
Figure 4 shows a partial sectional view of a detail of the clutch according to Fig. 3, seen along a line IV-IV; and
Figure 5 shows a partial axial plan view of a presser plate of the clutch according to Fig. 3, with the abutment ring removed.
Fig. 1 shows in solid lines a thrust plate unit 1 of a motor vehicle friction clutch, the clutch disc 3 of which, as also a fly-wheel 5 driven by the internal combustion engine of the motor vehicle, is represented in dot-anddash lines. The thrust plate unit 1 has a cover 7 secured in a manner not further illustrated to the fly-wheel, on which cover a presser plate 11 is guided fast in rotation but axially displaceably by means of several leaf springs 9 extending somewhat tangentially in relation to the axis of rotation of the clutch.A diaphragm spring 15 is held on the clutch cover 7 through a plurality of securing rivets 13 arranged along a common circle of arrangement and is supported radially outside the circle of arrangement of the rivets 13, in the region of its external circumference, through an abutment ring 17 enclosing the axis of rotation of the clutch, on the presser plate 11 of substantially annular disc form which likewise en closes- the axis of rotation of the clutch. The diaphragm spring 15 is supported on a knifeedge 19 of the abutment ring 17 and stresses the presser plate 11 through the clutch disc 3 against the fly-wheel 5. Fig. 1 shows the pertinent engaged state of the clutch.The presser plate 11 can be relieved of the spring force of the diaphragm spring 15 by means of a release system (not shown further), whereby the clutch disc 3, which in the engaged condition is clamped in between the presser plate 11 and the fly-wheel 5, is liberated and the clutch is released. In the clutch as illustrated in Fig. 1 the release system presses clutch fingers 21 of the diaphragm spring 15, which protrude radially of the axis of rotation, towards the fly-wheel 5, whereby the external circumference of the diaphragm spring 15, which is held tiltably on the securing rivets 13, moves axially away from the fly-wheel.
The- leaf springs 9, which guide the presser plate 11 on the clutch cover 7, are so initially stressed that they move (lift) the presser plate 11 axially away from the fly-wheel 5 and thus ensure correct disengagement of the friction clutch.
In-clutch operation the friction linings of the clutch disc 3, indicated at 23, wear away, whereby the presser plate 11 in the engaged condition approaches the fly-wheel 5. The approach influences the adjustment of the diaphragm spring 15 and also that of the clutch release system. The clutch is provided with two automatically acting adjusting devices which automatically compensate for the variations of position of the presser plate 11 caused by wear. A first adjusting device 25 automatically compensates for variations of distance between the presser plate 11 and the diaphragm spring 15. A second adjusting device 27 automatically compensates for variations of distance between the presser plate 11 and the stroke-limiting element 29 which limits the maximum lift-away stroke of the presser plate 11 in relation to the clutch cover 7.
The stroke-limiting element 29 has essentially the form of a sleeve which is-axially displaceable in an opening 31 of the clutch cover 7 over a predetermined stroke 37 limited by stop flanges 33, 35 in relation to the clutch cover 7. The stroke-limiting sleeve 29 is seated with clamp fit on a- radially resilient clamping sleeve 39, which in turn is axially fixed on a rivet bolt 41 protruding from the presser plate 11. On the side of the clutch cover 7 axially remote from the presser plate 11 the rivet bolt 41 carries a stop ring 43 cooperating with the stroke-limiting sleeve 29.
The stroke-limiting sleeve 29 is axially displaceable on overcoming of the retaining force exerted by the clamping sleeve 39. The lift-off force of the leaf spring 9 is less than this retaining force, so that the presser plate 11, when the clutch is disengaged, can be lifted away from the clutch disc 3 only by the stroke 37. On the other hand the force of the diaphragm spring 15 is greater than the retaining force of the clamping sleeve 39, so that the presser plate 11, in the case of wear of the friction linings 23, can be adapted automatically to the reducing thickness of the friction linings 23, despite the stroke limitation by the stroke-limiting sleeve 29. The stop ring 43 limits the maximum displacement distance of the presser plate 11.
The stroke-limiting sleeve 29 defines the liftoff position of the presser plate 11. However with increasing wear of the friction linings 23 the lift-off position departs from the ideal position which the external circumference of the diaphragm spring 15 should adopt when the clutch is in the disengaged condition. In order to compensate for this variation of distance the abutment ring 17 is guided axially displaceably but fixedly in the radial direction in an annular groove 45-which is axially open towards the diaphragm spring 15 and concentrically surrounds the axis of rotation of the clutch. The abutment ring 17 has in distribution over its circumference several slots or apertures 47 open towards the fly-wheel 5, which terminate in a bottom surface 49 perpendicular to the axis of rotation of the clutch.
Radially on both sides of the bottom surface 49 the annular groove 45 merges into support faces 51 extending obliquely of the bottom surface 49. The bottom surface 49 and the support faces SI, or the imaginary prolongations in each case, form a wedge gap tapering radially outwards away from the axis of rotation of the clutch, in which there is seated a wedge 53 which radially bridges over the annular groove 45. The wedge 53 supports the abutment ring 17 against the support faces 51 on both sides of the annular groove 45, while the position of the wedge 53, radially adjustable and radially limited by stops 55, fixes the axial position of the abutment ring 17 in relation to the presser plate 11.
The wedge 53 is fixed in the circumferential direction of the annular groove 45 by noses 57 and holds the abutment ring 17 fast in rotation but axially displaceably on the presser plate 11, since the width of the aperture 47 in the circumferential direction is made equal to the width of the wedge 53. The fixing of the abutment ring 17 fast in rotation acts against wear on the knife-edge 19 and the diaphragm spring 15.
The wedges 53, of which Fig. 1 shows only one, are guided radially freely movably in the apertures 47. On relieving of the abutment ring in the disengaged condition they are pressed outwards by the centrifugal force by reason of the rotation of the presser plate 11, whereby the presser ring 17 is automatically readjusted into the disengagement position of the diaphragm spring 15. In order to prevent returning of the wedges 53 on loading of the abutment ring 17 by the spring force of the diaphragm spring 15, the wedge angle between the faces 49 and 51 and the equally great wedge angle of the complementary, mutually opposite faces 59, 61 of the wedge 53, which co-operate with these faces, is of such small dimension that non-reversibility occurs.If necessary the wedges 53 can be initially stressed radially outwards by a comparatively weak spring (not further illustrated). This spring can be a common annular spring. The spring prevents the wedges 53 from shifting by reason of gravity if the abutment ring 17 is relieved of load with the presser plate stationary.
Other forms of embodiment and variants of motor vehicle friction clutches are to be explained below. Parts of like function are provided with like reference numerals, but with an additional letter for distinction. For explanation reference is made to the description of Fig. 1.
Fig. 2 shows details of a thrust plate unit 1a which differs from the thrust plate unit 1 according to Fig. 1 only in that an axially resilient corrugated ring 63, which initially stresses the abutment ring 1 7a axially towards the diaphragm spring 15a, is laid into the annular groove 45a. The centrifugal force acting upon the wedge 53a must therefore be able to move only the wedge, but not the abutment ring 17a as well.
The motor vehicle friction clutch according to Figs. 3 to 5 differs from the clutch according to Fig. 1 essentially only in the configuration of its adjusting device 25b which automatically adjusts the distance between the presser plate 11 b and the diaphragm spring 15b. The assembly of the thrust plate unit 1b and especially also of the adjusting device 27b which adjusts the stroke limitation correspond to the components as explained with reference to Fig. 1.
The abutment ring 1 7b is seated both rotatably about the axis of rotation of the clutch and axially displaceably in the annular groove 45b. It has a plurality of apertures 67 distributed in the circumferential direction and open towards the bottom surface 65 of the annular groove 45b. which extend over the entire radial width of the abutment ring 17b and are limited, oppositely to the bottom surface 65, by an oblique face 69 extending in the circumferential direction of the abutment ring 1 7b and obliquely in relation to the bottom surface 65b. In each of the apertures 67 a ball 70 is seated the diameter of which is larger than the radial width of the abutment ring 17b.The ball 70 engages, radially on both sides of the abutment ring 17b, in pockets 71 which are formed in the radial side walls of the annular groove 45b and fix the ball 70 in the circumferential direction of the annular groove. The faces 65, 69 lie against substantially diametrically opposite sides of the ball 70 and form a wedge gap which narrows in the circumferential direction of the abutment ring 17b. Oppositely to the direction of narrowing a compression spring 73 is clamped in the aperture 67 between the ball 70 and an end face 75 of the aperture 67. The compression spring 73 seeks to rotate the abutment ring 17b in a direction in relation to the presser plate 1 1b in which the abutment ring 1 7b is lifted towards the diaphragm spring 15b for the wear compensation. The angle between the faces 65, 69 is dimensioned so that non-reversibility occurs.
Claims (11)
1. Thrust plate unit for a motor vehicle friction clutch, comprising
a) a clutch cover (7),
b) a presser plate (11) of substantially annular disc form which is fast in rotation but axially movable in relation to the clutch cover (7), related to a common axis of rotation of the clutch,
c) a diaphragm spring (15) supported on the clutch cover (7) along a first diameter circle,
d) an abutment ring (17) guided axially movably on the presser plate (11) and having a knife-edge (19) on which the diaphragm spring (15) is supported along a second diameter,
e) a first adjusting device (25) fixing the axial relative position between the presser plate (11) and the abutment ring (17), having several oblique face-axial thrust means (49, 51, 53; 65, 69, 70) distributed in the circumferential direction of the abutment ring (17) for an automatic approach of the abutment ring (17) to the diaphragm spring (15) when the abutment ring (17) is relieved of the diaphragm spring (15) in clutch operation,
f) a disengagement device resiliently initially stressing the presser plate (11) axially towards the diaphragm spring (15) with a stroke-limiting element (29) which limits the disengagement stroke of the presser plate (11) in relation to the clutch cover (7),
g) an automatic second adjusting device (27) which fixes the axial relative position between the presser plate (11) and the stroke-limiting element (29) characterised in that the oblique face-axial thrust means each comprise a thrust body (53; 70) with mutually axially substantially opposite abutment faces (59, 61) on which there rest associated abutment faces (49, 51; 65, 69) of the presser plate (11) for the one part and of the abutment ring (17) for the other part, where at least two of these abutment faces (49, 51; 65, 69) extend obliquely in relation to one another at an angle effecting non-reversibility.
2. Thrust plate unit according to Claim 1, characterised in that the thrust body (53) is guided radially movably in relation to the axis of rotation of the clutch and the two abutment faces (49, 51) extending obliquely of one another extend towards one another radially away from the axis of rotation of the clutch.
3. Thrust plate unit according to Claim 2, characterised in that the thrust body is formed as a radially outwardly tapering wedge (53).
4. Thrust plate unit according to Claim 3, characterised in that the wedge (53) is radially displaceably guided in radially extending apertures (47, 57) of both the abutment ring (17) and of the presser plate (11) and connects the abutment ring (17) fast in rotation with the presser plate (11).
5. Thrust plate unit according to one of
Claims 2 to 4, characterised in that the thrust bodies (53) are formed as centrifugal weights.
6. Thrust plate unit according to one of
Claims 2 to 5, characterised in that the presser plate (11) comprises an annular groove (45) open axially towards the diaphragm spring (15), in which the abutment ring (17) is axially movably guided.
7. Thrust plate unit according to Claim 6, characterised in that a corrugated spring ring (63) which initially stresses the abutment ring (17a) axially towards the diaphragm spring (15a) is arranged in the annular groove (45a).
8. Thrust plate unit according to Claim 1, characterised in that the two abutment faces (65, 69) extending obliquely of one another extend towards one another in the circumferential direction of the abutment ring (17b) and of the presser plate (ill) and in that a spring (73) for the relative movement of the thrust body (70) and of at least one of the two abutment faces (69) extending obliquely of one another acts on each thrust body (70).
9. Thrust plate unit according to Claim 8, characterised in that the abutment faces (65, 69) of the abutment ring (17b) and of the presser plate (ill) form a wedge gap tapering in the circumferential direction and in that the thrust bodies are formed as balls (70).
10. Thrust plate unit according to Claim 9, characterised in that the presser plate (ill) comprises an annular groove (45b) axially open to the diaphragm spring (15b), in which the abutment ring (17b) is rotatably and axially movably guided, in that the diameter of the ball (70) is large than the radial width of the annular groove (45b), in that the ball (70) is arranged fixed in the circumferential direction of the annular groove (45b) in a radially widening pocket (71) of the annular groove (45b), and in that the spring (73) is clamped in between the ball (70) and a shoulder (75) of the abutment ring (17b).
11. A thrust plate unit as claimed in claim 1, substantially as described herein with reference to and as illustrated by any one of the examples shown in the accompanying drawings.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19853518781 DE3518781A1 (en) | 1985-05-24 | 1985-05-24 | SELF-ADJUSTING CLUTCH |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB8611610D0 GB8611610D0 (en) | 1986-06-18 |
| GB2176256A true GB2176256A (en) | 1986-12-17 |
Family
ID=6271603
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB08611610A Withdrawn GB2176256A (en) | 1985-05-24 | 1986-05-13 | Thrust plate unit for friction clutch |
Country Status (6)
| Country | Link |
|---|---|
| JP (1) | JPS61274122A (en) |
| DE (1) | DE3518781A1 (en) |
| ES (1) | ES8704242A1 (en) |
| FR (1) | FR2582363A1 (en) |
| GB (1) | GB2176256A (en) |
| IT (2) | IT8653444V0 (en) |
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5186298A (en) * | 1989-12-29 | 1993-02-16 | Kabushiki Kaisha Daikin Seisakusho | Clutch cover assembly |
| GB2264989A (en) * | 1992-03-10 | 1993-09-15 | Luk Lamellen & Kupplungsbau | Friction clutch |
| US5349882A (en) * | 1992-07-23 | 1994-09-27 | Kabushiki Kaisha Daikin Seisakusho | Clutch wear-compensating compound flywheel assembly |
| US5377803A (en) * | 1992-05-06 | 1995-01-03 | Fichtel & Sachs Ag | Pressure plate arrangement for a motor vehicle friction clutch |
| GB2284025A (en) * | 1993-11-04 | 1995-05-24 | Fichtel & Sachs Ag | Friction clutch with wear compensation |
| US5419418A (en) * | 1992-07-06 | 1995-05-30 | Kabushiki Kaisha Daikin Seisakusho | Clutch cover assembly |
| GB2294301A (en) * | 1991-11-26 | 1996-04-24 | Luk Lamellen & Kupplungsbau | Friction clutch |
| GB2261923B (en) * | 1991-11-26 | 1996-07-03 | Luk Lamellen & Kupplungsbau | Friction clutch |
| FR2733808A1 (en) * | 1995-05-02 | 1996-11-08 | Valeo | RETRACTABLE FRICTION CLUTCH |
| EP0795695A2 (en) * | 1996-03-14 | 1997-09-17 | Exedy Corporation | Clutch cover assembly with a wear compensation mechanism |
| ES2119654A1 (en) * | 1991-11-26 | 1998-10-01 | Luk Lamellen & Kupplungsbau | Friction clutch |
| FR2765289A1 (en) * | 1997-06-17 | 1998-12-31 | Valeo | Friction clutch, especially for motor vehicle |
| FR2769058A1 (en) * | 1992-07-11 | 1999-04-02 | Luk Lamellen & Kupplungsbau | CLUTCH GROUP |
| FR2794506A1 (en) * | 1999-06-03 | 2000-12-08 | Valeo | Friction clutch for motor vehicle has wear compensator formed by ramp surfaces between clutch pressure plate and secondary clutch contact faces |
| FR3016669A1 (en) * | 2014-01-21 | 2015-07-24 | Schaeffler Technologies Gmbh | FRICTION CLUTCH AND METHOD FOR MANUFACTURING A FRICTION CLUTCH |
Families Citing this family (29)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2548152Y2 (en) * | 1991-02-20 | 1997-09-17 | 株式会社エクセディ | Clutch cover assembly |
| DE4244995B4 (en) * | 1991-11-26 | 2005-05-19 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Car friction clutch with pressure disc - has wear compensation and operation to provide constant force and moment transfer |
| DE4244919C2 (en) * | 1991-11-26 | 1998-01-22 | Luk Lamellen & Kupplungsbau | Car friction clutch with pressure disc |
| US5634541A (en) * | 1992-03-05 | 1997-06-03 | Luk Lamellen Und Kupplungsbau Gmbh | Automatically adjustable friction clutch |
| DE4306505B4 (en) * | 1992-03-10 | 2004-01-29 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | friction clutch |
| DE4306688C2 (en) * | 1992-05-06 | 1996-08-08 | Fichtel & Sachs Ag | Automatic wear compensation for the pressure plate of a motor vehicle friction clutch |
| DE4322677B4 (en) * | 1992-07-11 | 2005-05-12 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | friction clutch |
| DE4345215B4 (en) * | 1992-07-11 | 2005-05-04 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Coupling unit with friction clutch coupling - has pressure plate movably connected to counter pressure plate and has no clearance between shifter and controls |
| JP2656197B2 (en) * | 1992-09-07 | 1997-09-24 | 株式会社エクセディ | Clutch cover assembly |
| USRE37746E1 (en) * | 1992-09-07 | 2002-06-18 | Exedy Corporation | Clutch cover assembly |
| EP0622559B1 (en) * | 1993-04-29 | 1996-06-12 | FICHTEL & SACHS AG | Friction clutch with self adjuster |
| GB2278894B (en) * | 1993-05-26 | 1997-12-24 | Luk Lamellen & Kupplungsbau | Friction clutch |
| US5690203A (en) * | 1993-11-04 | 1997-11-25 | Fichtel & Sachs Ag | Motor vehicle friction clutch with automatic wear adjustment |
| US5509518A (en) * | 1994-04-21 | 1996-04-23 | Valeo Clutches And Transmissions, Inc. | Diaphragm clutch assembly with wear compensator |
| DE4414471A1 (en) * | 1994-04-26 | 1995-11-02 | Hisao Dipl Ing Murase | Clutch system between engine and transmission |
| DE4442594B4 (en) * | 1994-11-30 | 2005-02-03 | Zf Sachs Ag | friction clutch |
| DE4447888B4 (en) * | 1994-11-30 | 2004-11-11 | Zf Sachs Ag | Friction clutch for motor vehicles - has automatic adjusting mechanism with guide ring to support membrane spring, and ring having staggered circumferential gaps |
| FR2765288B1 (en) * | 1997-06-17 | 1999-10-01 | Valeo | FRICTION CLUTCH WITH FRICTION LINING WEAR REPAIR DEVICE, PARTICULARLY FOR A MOTOR VEHICLE |
| DE19744513C2 (en) * | 1997-10-09 | 2003-06-18 | Zf Sachs Ag | Pressure plate assembly |
| GB2339602B (en) * | 1998-03-13 | 2002-08-07 | Sachs Race Eng Gmbh | Friction clutch |
| DE19825240C2 (en) * | 1998-03-13 | 2003-07-03 | Sachs Race Eng Gmbh | friction clutch |
| DE10158362A1 (en) * | 2001-11-28 | 2003-06-12 | Bayerische Motoren Werke Ag | Self-adjusting vehicle clutch, to allow for wear, has a spring loaded pin which moves out under centrifugal force to engage teeth in the adjustment ring to block any action when rotating above a given speed level |
| CN101317020B (en) | 2005-11-29 | 2011-08-31 | 卢克资产管理有限责任公司 | Clutch assembly |
| KR20080071573A (en) * | 2005-11-29 | 2008-08-04 | 루크 라멜렌 운트 쿠프룽스바우 베타일리궁스 카게 | Clutch unit |
| DE102009029499A1 (en) * | 2009-09-16 | 2011-03-24 | Zf Friedrichshafen Ag | Pressure plate assembly for friction clutch of motor vehicle, has positioning element executing positioning movement by centrifugal force effect, where positioning element has wear detecting area |
| DE102010034809B4 (en) * | 2009-09-24 | 2019-08-29 | Schaeffler Technologies AG & Co. KG | Friction clutch with transport lock |
| DE102010035120B4 (en) * | 2009-09-24 | 2019-09-12 | Schaeffler Technologies AG & Co. KG | Friction clutch with transport lock |
| DE102013204589A1 (en) * | 2012-04-03 | 2013-10-10 | Schaeffler Technologies AG & Co. KG | coupling system |
| CN110388388B (en) * | 2018-04-17 | 2022-12-02 | 舍弗勒技术股份两合公司 | Friction clutch |
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|---|---|---|---|---|
| GB1341086A (en) * | 1970-12-19 | 1973-12-19 | Daimler Benz Ag | Clutch adjusting arrangements |
| GB2004000A (en) * | 1977-09-06 | 1979-03-21 | Borg Warner | Wear compensator for belleville spring clutch |
| GB1563708A (en) * | 1975-12-16 | 1980-03-26 | Automotive Prod Co Ltd | Clutches |
| US4207972A (en) * | 1978-05-26 | 1980-06-17 | Borg-Warner Corporation | Automatic wear compensator for Belleville spring clutches |
-
1985
- 1985-05-24 DE DE19853518781 patent/DE3518781A1/en not_active Withdrawn
-
1986
- 1986-05-13 GB GB08611610A patent/GB2176256A/en not_active Withdrawn
- 1986-05-23 FR FR8607846A patent/FR2582363A1/en active Pending
- 1986-05-23 IT IT8653444U patent/IT8653444V0/en unknown
- 1986-05-23 ES ES555309A patent/ES8704242A1/en not_active Expired
- 1986-05-23 IT IT67428/86A patent/IT1203563B/en active
- 1986-05-24 JP JP61118440A patent/JPS61274122A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1341086A (en) * | 1970-12-19 | 1973-12-19 | Daimler Benz Ag | Clutch adjusting arrangements |
| GB1563708A (en) * | 1975-12-16 | 1980-03-26 | Automotive Prod Co Ltd | Clutches |
| GB2004000A (en) * | 1977-09-06 | 1979-03-21 | Borg Warner | Wear compensator for belleville spring clutch |
| US4207972A (en) * | 1978-05-26 | 1980-06-17 | Borg-Warner Corporation | Automatic wear compensator for Belleville spring clutches |
Cited By (27)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5186298A (en) * | 1989-12-29 | 1993-02-16 | Kabushiki Kaisha Daikin Seisakusho | Clutch cover assembly |
| ES2119654A1 (en) * | 1991-11-26 | 1998-10-01 | Luk Lamellen & Kupplungsbau | Friction clutch |
| GB2261923B (en) * | 1991-11-26 | 1996-07-03 | Luk Lamellen & Kupplungsbau | Friction clutch |
| GB2294301B (en) * | 1991-11-26 | 1996-07-03 | Luk Lamellen & Kupplungsbau | Friction clutch |
| GB2294301A (en) * | 1991-11-26 | 1996-04-24 | Luk Lamellen & Kupplungsbau | Friction clutch |
| GB2264989B (en) * | 1992-03-10 | 1996-06-12 | Luk Lamellen & Kupplungsbau | Friction clutch |
| GB2264989A (en) * | 1992-03-10 | 1993-09-15 | Luk Lamellen & Kupplungsbau | Friction clutch |
| FR2688559A1 (en) * | 1992-03-10 | 1993-09-17 | Luk Lamellen & Kupplungsbau | FRICTION CLUTCH. |
| US5377803A (en) * | 1992-05-06 | 1995-01-03 | Fichtel & Sachs Ag | Pressure plate arrangement for a motor vehicle friction clutch |
| US5419418A (en) * | 1992-07-06 | 1995-05-30 | Kabushiki Kaisha Daikin Seisakusho | Clutch cover assembly |
| US5570768A (en) * | 1992-07-06 | 1996-11-05 | Kabushiki Kaisha Daikan Seisakusho | Clutch cover assembly |
| US6000515A (en) * | 1992-07-11 | 1999-12-14 | Luk Lamellen Und Kupplungsbau Gmbh | Clutch assembly |
| FR2769058A1 (en) * | 1992-07-11 | 1999-04-02 | Luk Lamellen & Kupplungsbau | CLUTCH GROUP |
| US5349882A (en) * | 1992-07-23 | 1994-09-27 | Kabushiki Kaisha Daikin Seisakusho | Clutch wear-compensating compound flywheel assembly |
| US5469760A (en) * | 1992-07-23 | 1995-11-28 | Kabushi Kaisha Daikin Seisakusho | Clutch wear-compensating compound flywheel assembly |
| GB2284025A (en) * | 1993-11-04 | 1995-05-24 | Fichtel & Sachs Ag | Friction clutch with wear compensation |
| US5560463A (en) * | 1993-11-04 | 1996-10-01 | Fichtel & Sachs Ag | Friction clutch for a motor vehicle transmission and a friction clutch having automatic adjustment for wear |
| GB2284025B (en) * | 1993-11-04 | 1997-12-10 | Fichtel & Sachs Ag | Motor vehicle friction clutch |
| FR2733808A1 (en) * | 1995-05-02 | 1996-11-08 | Valeo | RETRACTABLE FRICTION CLUTCH |
| US5960926A (en) * | 1995-05-02 | 1999-10-05 | Valeo | Friction clutch with wear compensation |
| EP0795695A3 (en) * | 1996-03-14 | 1998-09-16 | Exedy Corporation | Clutch cover assembly with a wear compensation mechanism |
| US5904233A (en) * | 1996-03-14 | 1999-05-18 | Exedy Corporation | Clutch cover assembly having a wear compensation mechanism with diaphragm spring attitude control |
| US5971126A (en) * | 1996-03-14 | 1999-10-26 | Exedy Corporation | Clutch cover assembly having a wear compensation mechanism with diaphragm spring attitude control |
| EP0795695A2 (en) * | 1996-03-14 | 1997-09-17 | Exedy Corporation | Clutch cover assembly with a wear compensation mechanism |
| FR2765289A1 (en) * | 1997-06-17 | 1998-12-31 | Valeo | Friction clutch, especially for motor vehicle |
| FR2794506A1 (en) * | 1999-06-03 | 2000-12-08 | Valeo | Friction clutch for motor vehicle has wear compensator formed by ramp surfaces between clutch pressure plate and secondary clutch contact faces |
| FR3016669A1 (en) * | 2014-01-21 | 2015-07-24 | Schaeffler Technologies Gmbh | FRICTION CLUTCH AND METHOD FOR MANUFACTURING A FRICTION CLUTCH |
Also Published As
| Publication number | Publication date |
|---|---|
| IT1203563B (en) | 1989-02-15 |
| IT8667428A0 (en) | 1986-05-23 |
| FR2582363A1 (en) | 1986-11-28 |
| JPS61274122A (en) | 1986-12-04 |
| GB8611610D0 (en) | 1986-06-18 |
| IT8653444V0 (en) | 1986-05-23 |
| ES8704242A1 (en) | 1987-03-16 |
| ES555309A0 (en) | 1987-03-16 |
| DE3518781A1 (en) | 1986-11-27 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| WAP | Application withdrawn, taken to be withdrawn or refused ** after publication under section 16(1) |