GB2339000A - Disengagement device for vehicle clutch - Google Patents

Disengagement device for vehicle clutch Download PDF

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Publication number
GB2339000A
GB2339000A GB9905961A GB9905961A GB2339000A GB 2339000 A GB2339000 A GB 2339000A GB 9905961 A GB9905961 A GB 9905961A GB 9905961 A GB9905961 A GB 9905961A GB 2339000 A GB2339000 A GB 2339000A
Authority
GB
United Kingdom
Prior art keywords
disengagement device
particularly according
diaphragm spring
release bearing
compensating ring
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
GB9905961A
Other versions
GB2339000B (en
GB9905961D0 (en
Inventor
Norbert Mebus
Matthias Zink
Christoph Hirschle
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.)
LuK Lamellen und Kupplungsbau GmbH
Original Assignee
LuK Lamellen und Kupplungsbau 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 LuK Lamellen und Kupplungsbau GmbH filed Critical LuK Lamellen und Kupplungsbau GmbH
Publication of GB9905961D0 publication Critical patent/GB9905961D0/en
Publication of GB2339000A publication Critical patent/GB2339000A/en
Application granted granted Critical
Publication of GB2339000B publication Critical patent/GB2339000B/en
Anticipated expiration legal-status Critical
Expired - Fee Related 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
    • F16D23/143—Arrangements or details for the connection between the release bearing and the diaphragm
    • F16D23/144—With a disengaging thrust-ring distinct from the release bearing, and secured to the diaphragm
    • F16D23/145—Arrangements for the connection between the thrust-ring and the diaphragm
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/084—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface sliding on a complementary spherical surface
    • 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
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
    • F16D23/142—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings with a resilient member acting radially between the bearing and its guide means
    • 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
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
    • F16D23/143—Arrangements or details for the connection between the release bearing and the diaphragm
    • F16D23/144—With a disengaging thrust-ring distinct from the release bearing, and secured to the diaphragm
    • F16D23/146—Arrangements for the connection between the thrust-ring and the release bearing
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/43—Clutches, e.g. disengaging bearing

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Support Of The Bearing (AREA)
  • Rolling Contact Bearings (AREA)

Description

- I - 2339000 DISENGAGEMENT DEVICE The invention relates to a release
bearing for a clutch 5 preferably in motor vehicles.
Devices of this structural type generally consist of at least one release bearing which is mounted rotationally rigid on an axially displaceable sliding sleeve and which by means of a circumferential flange part which is formed as a contact pressure plate axially deflects a diaphragm spring which controls the engagement and disengagement of the clutch.
The axial displacement takes place through a disengagement lever or a central disengagement member wherein the disengagement movement can be introduced by means of a clutch pedal or automatically by means of a clutch actor.
The construction of the release bearing corresponds substantially to that of an axial bearing or an inclined ball bearing wherein each bearing ring has an angled flange part mounted at right angles to the axis of symmetry of the release bearing. A bearing ring is thereby connected rotationally rigid through the flange part to the axially displaceable operating member. The diaphragm spring tongues or disengagement lever of the clutch is supported on the flange part of the circumferential bearing ring which is aligned towards the clutch.
In the installed state the release bearing can be exposed to a so-called tongue shock, eg to an axial shock of the diaphragm springs which increases the wear on the release bearing and thus leads to a reduction in the service life.
This axial shock which is a condition of the manufacturing process and is caused inter alia by clutch diaphragm springs leads in the case of the disengagement systems previously mentioned to sealing problems and loss of 5 comfort.
Furthermore the two drive components which are separated by the clutch can have an axially parallel stagger between the f orce-transf erring shafts which has to be compensated by a self-centring of the release bearing parallel to the force- transferring shaft since otherwise the release bearing is exposed to increased wear and vibrations increase the loss of comfort.
various proposals have been put forward to compensate or balance a disadvantageous tongue shock of the kind mentioned and the axial stagger of the force-transf erring shafts.
DE U 72 45 141 discloses a release bearing assembly wherein a compensating ring is provided between the spring tongues of the diaphragm spring and the inner ring of the release bearing. The contact bearing face is formed spherical between the inner ring and compensating ring whereby the compensating ring can be displaced and thus aligned relative to the inner ring of the release bearing. A drawback with this proposed solution is inter alia a lack of a radial axially parallel compensation in the form of a radial self centring so that a stagger between the force-transferring shafts cannot be produced. Therefore a release bearing of the type disclosed tumbles about the spherical centre point of the ball-shaped centring ring since the release bearing is only mounted at this axial height by means of an elastic ring so that even here irregular running and associated vibrations are to be expected. A radial stagger of the compensating ring relative to the compensating bearing is not proposed so that the axial shock can only be compensated through an angular displacement of the release bearing itself.
The object of the invention is therefore to design a disengagement device so that compensation of the tongue shock of the diaphragm spring tongues is possible without additional devices on a release bearing and without an angular stagger of the release bearing opposite the axis of rotation.
This is achieved through a disengagement device for a clutch, preferably for motor vehicles, which consists at least of a release bearing mounted on a sliding sleeve and a diaphragm spring causing the engagement and disengagement processes of the clutch, whereby between the diaphragm spring and the release bearing there are two areas having complementary ball face segments and both are provided directly or indirectly on the diaphragm spring and the areas having the ball face segments are radially displaceable relative to the release bearing.
The component parts having the ball face segments are 25 preferably able to swivel relative to each other from the axis of rotation whereby a compensation of the tongue shock of the diaphragm springs is initially possible. The swivel area of the areas having the ball segments lies preferably between the angles 9 = 100, preferably 9= 1.50.
The subject of the invention can advantageously be designed so that it is free of the effect of the resetting forces which act on the areas having the ball face segments. Such effects particularly occur when elastic or non-elastic stops are used to restrict the swivel area of the two areas having the ball face segments. The disengagement devices according to the invention can advantageously be provided without these said stops.
A design according to the invention proposes the formation of the first area having a ball face segment whereby this is formed directly on the diaphragm spring tongues. To this end the radially inwardly aligned diaphragm spring tongues can be provided with the ball segment shaped profiled section during the production process by way of example through pressing, cold- forming, deep-drawing or the like - and where applicable treated with a subsequent hardening process - whereby it can be advantageous to imprint the ball segment in the direction of the clutch bell or in the direction of the release bearing. The complementary area having a ball face segment is then formed accordingly.
As the component which has the second ball face segment which is complementary with the first ball face segment it is possible to provide advantageously a compensating ring which can be mounted axially between the diaphragm spring and a flange part which is provided as a contact pressure plate of the release bearing wherein the compensating ring is structurally separate from the release bearing or can be fixed on component parts of the disengagement device secure against loss. A connection with non-revolving structural parts of the clutch, for example the clutch bell or the like can also be advantageous whereby the compensating ring is mounted and/or centred on this structural part.
According to the invention it is further advantageous to 35 connect the compensating ring to the diaphragm spring secure against loss. This has the advantage that a conventional release bearing can be used without further adaptation whereby the compensating ring and the flange part lie substantially flat on each other on their axially facing sides but can be displaced radially relative to each other.
The non-detachable fixing of the compensating ring on the diaphragm spring can be advantageously achieved through fastening means of the compensating ring which engage in gaps which separate the radially inwardly extending diaphragm spring tongues of the diaphragm spring. Advantageously at least two or more snap-fit noses are provided spread evenly over the circumference and engaging through the gaps between the diaphragm spring tongues. The snap-fit noses can be mounted in an embodiment according to the invention on the ball face segment. To secure the non-detachable fitting it is advantageous to provide a ball-shaped area on the snap-fit noses at their end remote from the compensating ring whereby the passage of the ball shaped snap-fit noses through the gaps can be made easier by an elastic design of the ball-shaped areas. A further embodiment is the formation of preferably central slits in the ball shaped ends of the snap-fit noses which as they press through the gaps allow the ends to compress which then spring back to their original shape. Here it is expedient to provide the slits in the direction of the path of the slits formed by the diaphragm spring tongues and to select an approximately conical shape at the ends so that after the snap-fit noses snap in, the wide cone base f orms a stop f or the diaphragm spring tongues.
In order to avoid high wear on the compensating ring and 35 with a suitable choice of material for the compensating ring at the diaphragm spring tongues it is advantageous to select the diameter of the necks of the snap-f it noses so that the diaphragm spring tongues which change the gap widths of the gaps formed between same during the course of their axial operating movement do not restrict the snap-fit noses, i.e. the diameter of the snap-fit noses is advantageously smaller than the minimum gap width during the entire axial operating stretch of the diaphragm spring since otherwise increased undefined wear and difficult running of the clutch would occur.
An advantageous design of the subject of the invention provides materials for the compensating ring which allow rapid production techniques with high numbers, by way of example an injection casting process. A plastics is preferably used here which in this area is therTnally and mechanically resistant, such as for example polyamide with or without glass fibre reinforcement.
Furthermore an embodiment is advantageous having a radially selfadjusting release bearing which can compensate independently of the tongue shock of the diaphragm spring a stagger of the force-transferring axes, that is this embodiment can with the means according to the invention compensate on the one hand an angular stagger acting on the release bearing, caused inter alia by a tongue shock and/or unevenly mounted clutch cover and on the other hand a parallel stagger of the forcetransferring shafts for example caused by non-central mounting.
The invention will now be explained with reference to Figures 1 and 2 in which:
Figure 1 shows a sectional view through an embodiment of the subject of the invention; Figure 2 is a view of a compensating ring; and Figure 3 is a partial view of a compensating ring with diaphragm spring tongues placed thereon in the direction of the arrow in Figure 1.
Figure 1 shows a disengagement device 1 consisting of a sliding sleeve 2 connected rotationally rigid to the gearbox housing (not shown) and mounted about a gear input shaft (not shown). A disengagement piston 3 of a central disengagement member (not shown in further detail) is mounted rotationally rigid but axially displaceable on the sliding sleeve. To reduce the friction forces during axial displacement the disengagement piston 3 is provided on its inner circumference with axially aligned grooves 4. A release bearing 5 is mounted around the disengagement piston 3 and is connected by the bearing ring G rotationally rigid to the disengagement piston 3 and is fixed in the axial direction by means of a snap-fit closure 7 provided on the end of the disengagement piston 3 pointing in the direction of the clutch. A bearing shell 8 is supported in the axial direction on the bearing ring 7 and is centred against the action of the spring 9. A further spring 10 is supported on the radially outwardly curved flange 11 of the bearing ring 6 and on the spring 9 so that the bearing shell 8 as well as the rolling bodies 12 adjoining same radially inwards and the radially adjoining circumferential flange part 13 forming the bearing shell 13a are displaceable radially against the spring forces of the springs 9, 10. In this way with slight axial pretension of the release bearing a radial stagger is possible parallel to the gear input shaft and thus a compensation of the stagger is possible between the gear input shaf t and a drive shaft (not shown) which in non-compensated cases causes turning irregularities on the disengagement devices and their following structural parts by way of example the disengagement member, pedals, hydraulic devices etc.
In this way the release bearing 5 is adjusted with slight axial pretension whilst with greater pretension during the engagement and disengagement processes the bearing shell 8 is pressed against the bearing ring 6 and therefore the adjusted radial position remains set.
The flange part 13 has in the direction remote from the rolling bodies 12 a radially outwardly bent flange 14 which is provided axially flat and forms the contact bearing face 17 for the compensating ring 15 which has in turn an axially approximately flat contact bearing face 16. Both contact bearing faces 16, 17 are displaceable radially relative to each other.
The compensating ring 15 has on its side opposite the contact bearing face 16 a ball-shaped surface segment 18 with radius R which intersects the axis of rotation 19 of the compensating ring 15. The diaphragm spring tongues 21 of the diaphragm spring which is held by the clutch housing 23 and which is not shown in its entirety have at their radially inner ends surface segments 20 which are substantially complementary with the surface segments 18 of the compensating ring 15 wherein the surface segments 18, 20 are displaceable relative to each other on the ball surface 22.
A tongue shock of the diaphragm spring tongues 21 shows itself in that the ball face segment 20 formed by the diaphragm springs 21 no longer adjoins the ball face segment 18 formed by the compensating ring 15 over the entire circumference. The compensating ring 15 is therefore radially displaced in the direction in which the axial distance from the diaphragm spring tongues is greatest whereby at the same time through the shape of the ball face segments 18 an increase in the axial distance to the diaphragm spring tongues 21 occurs without tongue shock. The axial play thereby arising is imitated by the disengagement piston 3.
The result of the compensation of the tongue shock is for the rotational axis 19 of the compensating ring 15 a radial parallel displacement relative to the axis of rotation of the gear input shaft. A parallel axial stagger between the drive shaft and gear input shaft is compensated by radial displacement of the release bearing 5.
The compensating ring 15 is connected secured against loss 20 to the diaphragm spring tongues 21 by means of snap-fit noses 24.
Figures 2 and 3 show for a more detailed explanation the compensating ring 15 with snap-fit noses 25 spread evenly over the circumference and projecting on the ball face segment 18 substantially at right angles to a tangent placed along the ball segment surface. The snap-fit noses have a neck 25 adjoined by a ball-shaped area 26 which has along the longitudinal extension of the diaphragm spring tongues slits 27 so that when the snap-fit noses pass through the radially inwardly aligned slits 28 which are formed by the diaphragm spring tongues 21 the slit ball shaped areas can be compressed and snap out again after passing through so that by their ball-shaped areas 2G forming stops they fix the compensating ring 15 secured against loss on the diaphragm spring tongues 21.
The width of the slits 28 between the diaphragm spring tongues 21 is changed by axial movements of the diaphragm spring during the engagement and disengagement processes so that the diameter of the necks 25 is matched to the minimum width of the slits 28.
The compensating ring 15 is preferably made by injection moulding plastics, for example glass fibre reinforced polyamide.
The patent claims filed with the application are proposed wordings without prejudice for obtaining wider patent protection. The applicant retains the right to claim further features disclosed up until now only in the description and/or drawings.
References used in the sub-claims refer to further designs of the subject of the main claim through the features of each relevant sub-claim; they are not to be regarded as dispensing with obtaining an independent subject protection for the features of the sub-claims referred to.
The subjects of these sub-claims however also form independent inventions which have a design independent of the subjects of the preceding claims.
The invention is also not restricted to the embodiments of the description. Rather numerous amendments and modifications are possible within the scope of the invention, particularly those variations, elements and combinations and/or materials which are inventive for example through combination or modification of individual features or elements or process steps contained in the drawings and described in connection with the general description and embodiments and claims and which through combinable features lead to a new subject or to new process steps or sequence of process steps insofar as these refer to manufacturing, test and work processes.

Claims (20)

1. Disengagement device for a clutch preferably for motor vehicles consisting at least of a release bearing mounted on a sliding sleeve and a diaphragm spring associated with the clutch and in active connection with the release bearing, with the following features:
a) two areas having complementary ball face segments are provided between the diaphragm spring and release bearing; b) both areas having ball face segments are provided directly or indirectly on the diaphragm spring; c) the areas forming the ball face segments are radially displaceable towards the release bearing.
2. Disengagement device more particularly according to claim I and/or 2 characterised in that the two areas having the ball face segments are able to swivel relative to each other.
3. Disengagement device more particularly according to claim I characterised in that the component parts having the ball face segments are free of the action of resetting forces acting on the swivel area.
4. Disengagement device more particularly according to one of the preceding claims, characterised in that the two areas having the ball face segments can swivel relative to each other preferably in an angular range of 9 10, preferably 9 = 1.5 degs.
5. Disengagement device more particularly according to one of the preceding claims, characterised in that the first area having a ball face segment is formed by tongues 35 of the diaphragm spring.
- 13
6. Disengagement device more particularly according to one of the preceding claims characterised in that the second area having a ball face segment is formed in a compensating ring mounted axially between the diaphragm spring and a flange part provided as a contact pressure plate of the release bearing.
7. Disengagement device more particularly according to one of the preceding claims characterised in that the compensating ring is separated structurally from the release bearing.
8. Disengagement device more particularly according to one of the preceding claims characterised in that the compensating ring is connected to the diaphragm spring secure against loss.
9. Disengagement device more particularly according to one of the preceding claims characterised in that the compensating ring and the flange part are approximately flat on their axially facing sides and are displaceable radially towards each other.
10. Disengagement device more particularly according to one of the preceding claims characterised in that fastening means of the compensating ring engage in gaps which are formed between the radially inwardly extending diaphragm spring tongues of the diaphragm spring.
11. Disengagement device more particularly according to one of the preceding claims characterised in that the fastening means consist of at least two snap-fit noses mounted on the ball face segment and engaging through the gaps between the diaphragm spring tongues.
12. Disengagement device more particularly according to one of the preceding claims characterised in that the snap-fit noses have a ball shape at their end remote from 5 the compensating ring.
13. Disengagement device more particularly according to one of the preceding claims characterised in that the snap fit noses are elastic.
14. Disengagement device more particularly according to one of the preceding claims characterised in that the snap fit noses are slit at their end remote from the compensating ring approximately in the middle in the direction of the path of the gaps.
15. Disengagement device more particularly according to one of the preceding claims characterised in that the diameter of the snap f it noses is smaller in the area of the passage through the gaps between the diaphragm spring tongues than the smallest gap width of the gaps between the diaphragm spring tongues which appears during the path of an axial displacement of the diaphragm spring.
16. Disengagement device more particularly according to one of the preceding claims characterised in that the compensating ring consists of plastics.
17. Disengagement device more particularly according to one of the preceding claims characterised in that the plastics is reinforced with glass fibre.
18. Disengagement device more particularly according to one of the preceding claims characterised in that the plastics is a glass fibre reinforced polyamide.
19. Disengagement device more particularly according to one of the preceding claims characterised in that the release bearing is radially self-centring. 5
20. Disengagement device for a clutch substantially as herein described with reference to the accompanying drawings.
GB9905961A 1998-03-20 1999-03-17 Release device Expired - Fee Related GB2339000B (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19812428 1998-03-20
DE19823759 1998-05-28
DE19823763 1998-05-28

Publications (3)

Publication Number Publication Date
GB9905961D0 GB9905961D0 (en) 1999-05-05
GB2339000A true GB2339000A (en) 2000-01-12
GB2339000B GB2339000B (en) 2002-09-25

Family

ID=27218228

Family Applications (2)

Application Number Title Priority Date Filing Date
GB9905960A Expired - Fee Related GB2338766B (en) 1998-03-20 1999-03-17 Release bearing
GB9905961A Expired - Fee Related GB2339000B (en) 1998-03-20 1999-03-17 Release device

Family Applications Before (1)

Application Number Title Priority Date Filing Date
GB9905960A Expired - Fee Related GB2338766B (en) 1998-03-20 1999-03-17 Release bearing

Country Status (5)

Country Link
KR (2) KR100581779B1 (en)
BR (2) BR9902336A (en)
DE (2) DE19912432B4 (en)
FR (2) FR2776350B1 (en)
GB (2) GB2338766B (en)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2815388A1 (en) * 2000-10-16 2002-04-19 Schaeffler Waelzlager Ohg Self-adjusting disengagement bearing for a clutch disengagement system of a motor vehicle comprises a pivotable adjustment ring which is supported on the inner race and supports the cup spring rim of the clutch
FR2818714A1 (en) * 2000-12-22 2002-06-28 Schaeffler Waelzlager Ohg CLUTCH THRUST BEARING
DE10125691A1 (en) * 2000-12-22 2002-07-04 Ina Schaeffler Kg Disengagement bearing for clutches of motor vehicles comprises a bearing disk which is mounted on a ring flange, and is made of a material reducing friction and optimizing wear
WO2002095250A1 (en) * 2001-05-18 2002-11-28 Ina-Schaeffler Kg Self-adjusting clutch release bearing
US6997619B2 (en) 2002-06-20 2006-02-14 Zf Sachs Ag Clutch release mechanism with a device for compensating for lack of precision in a friction clutch of a motor vehicle
CN102459939A (en) * 2009-04-27 2012-05-16 Skf公司 A ball bearing, a clutch thrust bearing including such a bearing, and a motor vehicle fitted with such a bearing

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DE19949909B4 (en) * 1999-10-16 2009-04-16 Schaeffler Kg Self-adjusting release bearing
DE10114845B4 (en) 2001-03-24 2012-05-31 Schaeffler Technologies Gmbh & Co. Kg Self-adjusting clutch release bearing
DE10114846A1 (en) * 2001-03-24 2002-10-02 Ina Schaeffler Kg Self-adjusting clutch release bearing
DE10114844B4 (en) * 2001-03-24 2013-02-28 Schaeffler Technologies AG & Co. KG Self-adjusting clutch release bearing
FR2836969B1 (en) * 2002-03-06 2004-07-09 Skf Ab CLUTCH CONTROL SYSTEM FOR A MOTOR VEHICLE AND DRIVE DEVICE THEREOF
DE50203756D1 (en) 2002-05-31 2005-09-01 Zf Sachs Ag Releaser with a device to compensate for inaccuracies in a friction clutch of a motor vehicle
EP1369611A1 (en) 2002-06-07 2003-12-10 ZF Sachs AG Clutch release with an inaccuracy-compensating device for a motor vehicle friction clutch
DE10233449A1 (en) * 2002-07-24 2004-01-29 Ina-Schaeffler Kg Clutch
DE102005024749A1 (en) * 2005-05-31 2006-12-07 Schaeffler Kg Release bearing of a shift disconnect clutch
FR2894308B1 (en) * 2005-12-06 2009-06-05 Valeo Embrayages CLUTCH SUB-ASSEMBLY, IN PARTICULAR FOR MOTORCYCLES, AND CLUTCH COMPRISING SUCH A SUBSET
DE102007010935A1 (en) * 2007-03-07 2008-09-11 Schaeffler Kg Clutch
DE102007020109A1 (en) 2007-04-28 2008-10-30 Schaeffler Kg clutch release
DE102009011249B4 (en) 2008-03-13 2021-08-26 Schaeffler Technologies AG & Co. KG Connection of a central slave cylinder to a clutch
DE102009016292A1 (en) 2008-04-17 2009-10-29 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Clutch actuating system, has coupling device comprising coil spring mechanism that includes coil spring of rectangular cross section, where coil spring comprises spring coils which lie on block
EP2146108A1 (en) 2008-07-16 2010-01-20 ZF Friedrichshafen AG Release device with a coupling element for operating a friction clutch in a motor vehicle
FR2936033B1 (en) * 2008-09-16 2011-06-10 Skf Ab BEARING BEARING, ITS USE AND MOTOR VEHICLE EQUIPPED WITH SUCH A BEARING.
DE102008042217A1 (en) 2008-09-19 2010-04-01 Zf Friedrichshafen Ag Release device for actuating friction clutch of motor vehicle, has carrier element fixed at friction clutch and arranged coaxial to rotational axis, and retaining element integratedly formed with release element
DE102009043242A1 (en) 2008-10-27 2010-04-29 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Clutch unit for use in motor vehicle for transmitting torque e.g. from engine to transmission, has slave cylinder radially and axial movably supported together with release piston and release bearing in clutch unit
DE102008063602A1 (en) 2008-12-18 2010-02-11 Schaeffler Kg Release bearing for clutch device, has pivot joint device comprising roll body collar with rolling bodies i.e. rollers, that follow one another in circumferential direction of roll body collar
DE102009020861A1 (en) * 2009-05-12 2010-11-18 Schaeffler Technologies Gmbh & Co. Kg Clutch actuation bearing, in particular for a dual clutch system
DE102010025334A1 (en) 2009-07-27 2011-02-03 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Central releaser for actuating friction clutch in drive train of motor vehicle for selectively separating and connecting two power transmission shafts, has annular piston divided into two rear- and front piston portions in axial direction
FR2950407B1 (en) 2009-09-23 2012-04-27 Skf Ab CLUTCH STOPPING DEVICE.
DE102010000847A1 (en) 2010-01-13 2011-07-14 ZF Friedrichshafen AG, 88046 Disengaging device for operating friction clutch of motor vehicle, has adjusting ring formed as ball ring in region of contact zone and arranged radially outside and partially within axial extent of clutch release sleeve
DE102010021035B4 (en) 2010-05-19 2018-06-07 Audi Ag Release or engagement device for friction clutches
DE102011086841A1 (en) 2010-12-20 2012-06-21 Schaeffler Technologies Gmbh & Co. Kg Central releasing unit, particularly for actuating friction clutch in drive train of motor vehicle for selectively separating and connecting two shafts, has housing that is concentrically arranged around drive shaft
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CN104755780B (en) * 2012-11-07 2017-09-08 舍弗勒技术股份两合公司 Hydraulic cylinder, the hydraulic cylinder in particular for the clutch operating device in motor vehicles
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DE102013202538A1 (en) 2013-02-18 2014-08-21 Schaeffler Technologies Gmbh & Co. Kg Clutch release bearing for switching separation clutches of motor car, has seals used to seal annular space and extended toward rotational axis towards ends to completely penetrate hole that is opened into space between seal and flange
DE102013203016A1 (en) 2013-02-25 2014-08-28 Schaeffler Technologies Gmbh & Co. Kg Clutch
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FR2776350B1 (en) 2001-08-31
GB2338766B (en) 2002-12-31
DE19912431A1 (en) 1999-09-23
FR2776351B1 (en) 2003-10-03
KR100581779B1 (en) 2006-05-24
DE19912431B4 (en) 2010-04-15
GB2338766A (en) 1999-12-29
FR2776350A1 (en) 1999-09-24
GB9905960D0 (en) 1999-05-05
BR9902337A (en) 1999-12-28
FR2776351A1 (en) 1999-09-24
DE19912432A1 (en) 1999-09-23
GB2339000B (en) 2002-09-25
KR19990078092A (en) 1999-10-25
DE19912432B4 (en) 2008-05-15
BR9902336A (en) 1999-12-28
KR100627498B1 (en) 2006-09-22
GB9905961D0 (en) 1999-05-05
KR19990078093A (en) 1999-10-25

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