GB2137292A - Friction clutch - Google Patents

Friction clutch Download PDF

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Publication number
GB2137292A
GB2137292A GB08407816A GB8407816A GB2137292A GB 2137292 A GB2137292 A GB 2137292A GB 08407816 A GB08407816 A GB 08407816A GB 8407816 A GB8407816 A GB 8407816A GB 2137292 A GB2137292 A GB 2137292A
Authority
GB
United Kingdom
Prior art keywords
clutch
plate
carrier plate
pressure plate
towards
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
GB08407816A
Other versions
GB8407816D0 (en
GB2137292B (en
Inventor
Albert Birk
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 GB8407816D0 publication Critical patent/GB8407816D0/en
Publication of GB2137292A publication Critical patent/GB2137292A/en
Application granted granted Critical
Publication of GB2137292B publication Critical patent/GB2137292B/en
Expired legal-status Critical Current

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00Friction clutches
    • F16D13/58Details
    • F16D13/70Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
    • F16D13/71Pressure 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00Friction clutches
    • F16D13/22Friction clutches with axially-movable clutching members
    • F16D13/38Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/46Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs in which two axially-movable members, of which one is attached to the driving side and the other to the driven side, are pressed from one side towards an axially-located member
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00Friction clutches
    • F16D13/58Details
    • F16D2013/581Securing means for transportation or shipping
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00Friction clutches
    • F16D13/58Details
    • F16D13/70Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
    • F16D2013/706Pressure 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00Special features for couplings or clutches
    • F16D2300/24Concentric actuation rods, e.g. actuation rods extending concentrically through a shaft

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

A friction clutch for a motor vehicle, has a clutch carrier plate (3) which can be secured to the crankshaft (2) of an engine, an axially movable pressure plate (4), a diaphragm spring (5) disposed between the pressure plate (4) and the clutch carrier plate (3) bearing with radially outward regions against the clutch carrier plate (3) and with radially further inwardly disposed regions against the pressure plate (4). Leaf springs (26) connect the pressure plate (4) and the clutch carrier plate (3). A counterpressure plate (12) is axially and non-rotatably secured to the clutch carrier plate (3) by way of spacer means (13). A clutch plate (10, 11) is disposed between the pressure plate (4) and the counterpressure plate (12). To make such friction clutches smaller or with given conditions in respect of space to increase the friction diameter and thus the working capacity of the clutch, the usual leaf spring elements (26) for torque transmission are disposed on that exterior face, which is towards the engine side (2) of the clutch. The pressure plate may include abutment surfaces 32 facilitating connection of the leaf springs by rivets 3a, and locator pin (43) may also be provided. The leaf springs may abut the carrier plate to limit their deformation. <IMAGE>

Description

SPECIFICATION Friction clutch The invention relates to a friction clutch, in particular for motor vehicles, comprising a clutch carrier plate which can be secured to the crankshaft of an engine, an axially movable pressure plate, a diaphragm spring which is disposed between the pressure plate and the clutch carrier plate and which bears with radially outward regions against the clutch carrier plate and which engages the pressure plate with radially further inwardly disposed regions, wherein torque transmission means are provided between the pressure plate and the clutch carrier plate, a counterpressure plate which can be axially and non-rotatably secured to the clutch carrier plate by way of spacer means, and a clutch plate which is to be disposed- between the counterpressure plate and the counterpressure plate.
In such friction clutches, torque is transmitted between the clutch carrier plate or the axially fixed counterpressure plate which is connected thereto, and the pressure plate, by way of leaf or plate spring elements which are connected on the pressure plate side to cams or projections provided at that location, projecting radially beyond the friction surfaces, on the one hand, and on the other hand, to fixing points which are likewise provided radially outwardly of the friction surface, on the clutch carrier plate or the counterpressure plate. As a result, friction clutches of that kind require a relatively large amount of space and, under given conditions, it is not possible to increase the friction diameter.
The present invention was based on the problem of reducing the amount of space required by friction clutches of that kind in the radial direction or, with given conditions of installation, increasing the friction diameter, in addition also providing a possible way of reducing the amount of space required in the axial direction, at least in regard to the internal space requirement of the clutch, and additionally designing such friction clutches so as to be more reliable in operation and less expensive to produce.
According to the present invention, that is achieved in that, in friction clutches of the kind set forth in the opening part of this specification, the torque transmission means are provided in the form of per se known plate springs on the outside space, which is towards the engine, of the clutch.
That makes it possible for the plate springs not to have to be disposed on radially outwardly directed projections, as hitherto, but instead the pressure plate may be provided with lugs or projections which face axially towards the engine and which extend through the clutch carrier plate through apertures therein and which are disposed at least substantially within the radial extent of the friction linings of the clutch plate. In that arrangement, the fixing locations on the lugs are desirably formed as end faces which are parallel to the plane of rotation of the clutch and the fixing location of the plate springs on the clutch carrier plate is also desirably disposed on the outward side, which is towards the engine side, of the clutch.Besides the amount of space required in the radial direction being reduced by virtue of that construction, the amount of space required in the axial direction is also less because the axial construction space which the plate springs would occupy if they were provided in the space between the clutch carrier plate and the pressure plate can be saved, and likewise in regard to the space required in the axial direction for the rivet head required for fixing purposes. Moving the plate springs into the space outside the clutch, in accordance with the invention, also affords the advantage of a considerably lower temperature loading, which makes itself apparent by virtue of lower setting losses in respect of the plate springs and thus reliability in operation of the clutch and an increased service life.In addition, such a construction, in comparison with a construction wherein the plate springs would be disposed in the space inside the clutch, that is to say, axially between the clutch carrier plate and the pressure plate, affords the advantage that, with the construction according to the invention, the diameter of the diaphragm spring is not limited by the plate springs. That means that the plate springs may also lie at least partially radially inwardly of the outside diameter of the diaphragm spring.
The friction clutch according to the invention is also desirably of such a configuration that the support for the diaphragm spring on the clutch carrier plate is disposed radially between the lugs which extend in the axial direction, and the support on the pressure plate.
It is also advantageous for the fixing location of the plate springs, on the clutch carrier plate side, also to be disposed on a bulged portion, which is formed out towards the engine, in the clutch carrier plate, while a bulged portion which is formed in a direction towards the counterpressure plate is formed in the clutch carrier plate, in the region of the lugs, thereby also ensuring a construction which is of short length in the axial direction.
It may also be advantageous for the region of the clutch carrier plate, which is adjacent to the fixing region of the lugs, on the pressure plate side-as viewed in the direction in which the plate spring extends to the fixing region at the clutch carrier plate side--serves as an abutment for the plate springs.In that arrangement, the abutment is disposed in such a relationship to the plate springs that the plate springs bear against that region at least approximately upon reaching the maximum degree of wear of the friction linings of the clutch, or are disposed in such a relationship that the abutments represent a safety means to prevent over-stretching of the plate springs when the unit comprising the pressure plate/diaphragm spring/clutch carrier plate is in a pre-assembled condition, for example during transportation or during assembly operations or however in an assembled condition on the crankshaft, without the counterpressure plate.
The abutment regions are desirably formed by calibration so as to ensure a high degree of accuracy of the abutment regions relative to each other.
A construction which is particularly advantageous in regard to assembly of the arrangement is provided when, in accordance with an additional feature of the invention, a flat face of the pressure plate is disposed in opposite relationship to the fixing rivets for the plate springs, after the clutch carrier plate, the flat face on the pressure plate serving as a support face for the riveting operation. In that arrangement, the support face may serve for forming the closure head during the riveting operation or may serve as a support means for the setting head when the closure head is formed on the outward side, which is towards the engine, of the clutch.In that arrangement, the support face is desirably disposed at such a spacing from the closure or setting head which is theretowards that at least a spacing corresponding to the disengagement lift motion of the pressure plate is provided therebetween.
As already mentioned in the preamble to this specification, the counterpressure plate is axially and non-rotatably fixed to the clutch carrier plate by way of spacer means, that is to say, means which bridge the axial spacing between the counterpressure plate and the clutch carrier plate. The space bridging means may be axially directed arm portions which are cast in one piece on the counter-pressure plate which comprises grey cast iron or spheroidal cast iron, or may be formed by an intermediate ring which is disposed between the clutch carrier plate and the counterpressure plate.A method of mounting the clutch on the engine that has been found to be particularly advantageous is one in which the pre-assembled unit of pressure plate/diaphragm spring/clutch carrier plate, which is held together by way of plate or leaf springs, is screwed to the crankshaft of the engine, whereupon the pressure plate is secured to the tongue portions of the diaphragm spring and then the counterpressure plate is secured to the clutch carrier plate, with the clutch plate interposed. As the counterpressure plate must be installed in a predetermined position with respect to the pre-assembled unit of the pressure plate, diaphragm spring and clutch carrier plate, a centering pin is provided, which is effective between those components.
In accordance with a further advantageous embodiment of a friction clutch according to the invention, the centering pin, for centering the spacer means, is provided in the direct vicinity of the fixing location of the plate springs. The centering pin used may be for example a dowel pin or a clamping sleeve, which is fitted in the clutch carrier plate, while it is also advantageous for the centering pin to be at least partially covered by the plate springs, in the radial direction, on the outward side, which is towards the engine, of the clutch carrier plate. That ensures in a particularly simple manner that the centering means cannot be moved or pushed out during the assembly operation.
However, the centering pin may also be fixed in the same region of the clutch carrier plate as the rivet which is used for fixing the plate or leaf springs to the clutch carrier plate.
In that arrangement, it may be particularly advantageous for the plate spring fixing rivet and the centering pin to be formed by a common element. In that respect, the combined element, on the side of the clutch carrier plate which is towards the transmission, may have the centering region which is of a pin-like configuration, and a shoulder with which the combined element bears against the clutch carrier plate, while it may also have a portion which extends through the clutch carrier plate and the plate springs on the side which is towards the engine and, adjoining same, the closure head which is formed by a riveting operation.
The plate or leaf springs may be secured to the pressure plate for example by way of screws which are fitted in blind bores in the region of the lugs. A manufacturing option which is particularly compact or convenient and easy to fit and thus inexpensive can be provided by the plate springs being fixed on the pressure plate side by means of a blind rivet connection which is provided in the lugs.
In that arrangement, use may be made of a hollow rivet element which is fitted into a blind bore provided in the lugs, with at least a portion of the section, which is in the blind bore, of the rivet element, being spread radially towards the contours of the blind bore. In that arrangement, the blind bores advantageously have an undercut configuration or profiled configuration which increases its diameter and which may be formed for example by a screwthread and into which the rivet element is plastically deformed by being radially expanded. A particularly advantageous blind rivet connection is formed by a hollow rivet element which is introduced into the blind bore being expanded or spread in the radial direction by driving in a spreader pin which remains in the bore in the rivet element.At its end which is towards the friction surface, the spreader pin is desirably of a tapered, spherical, cap-like or similar configu ration. A portion which projects beyond the plate springs in the direction of the engine side is deformed towards the plate springs, and thus forms the closure head, either simultaneously with or after the operation of driving in the spreader pin. In that connection, it is particularly advantageous for the spreader pin, at its region which is remote from the friction surface, also to have a tapering portion, for example a spherical, cap-shaped, conical or like portion onto which deformation is effected in a radial direction, to give the closure head, so that the spreader pin is thereby virtually embedded.
The invention will now be described in greater detail with reference to Figures 1 to 4.
In the drawings: Figure 1 shows a view in section taken along line ll-ll in Figure 1, Figure 2 shows a view from the direction of the arrow II in Figure 1, Figure 3 shows a view in section taken along line Ill-Ill in Figure 2, and Figure 4 shows a further detail in accordance with the invention.
The friction clutch 1 comprises a clutch carrier plate 3 which is secured to the crankshaft 2 of which part is shown, an axially movable pressure plate 4, a diaphragm spring 5 which is disposed between the pressure plate 4 and the clutch carrier plate 3 and which bears with radially outward regions 6 against support regions 7 of the clutch carrier plate 3 and which engages the pressure plate 4 by way of support projections 9, at radially further inwardly disposed regions 8.The diaphragm spring 5 is installed in the prestressed condition and loads the friction linings 10 of the clutch plate 11 towards the counterpressure plate 1 2 which is axially fixedly and non-rotatably connected to the clutch carrier plate 3 by way of a spacer or spacing bridge means 1 3. The spacer means 1 3 is a sheet metal member which is of a hat-like or cup-like configuration and which is secured to the clutch carrier plate 3 by way of the edge portion 14 of the member 13, by means of set screws 1 5. The screws 1 5 also secure in position the toothed ring 1 6 which is pushed or pressed onto the at least approximately axially extending portions 1 7 of the sheet metal member 1 3. The counterpressure plate 1 2 is pressed into the hat-like or cup-like spacer member 1 3 and has radially directed portions 1 8 which clampingly engage over the counterpressure plate so that in that way the pressure plate is fixed in the axial direction.Groove-like or channel-like portions 1 9 which engage from the at least approximately axially extending portions of the sheet metal member 1 3 radially inwardly into portions 20 in the.counterpressure plate, which are also of a groove-like or channel-like configuration, ensure that the counterpressure plate 1 2 is satisfactorily fixed in the hat-shaped or cupshaped member in the peripheral direction.
The clutch is engaged and disengaged by way of a central pushrod 21 which actuates a pressure disc 22 and thereby the diaphragm spring 5.
The pressure plate 4 has axial projections or lugs 23 which are disposed at least substantially within the radial extent of the friction linings 10 and which pass through the clutch carrier plate 3 through apertures 24 therein.
An end face 25 of the lugs 23 serves as a fixing location for the leaf or plate springs 26 which are disposed outside the clutch space defined by the clutch carrier plate 3 on the one hand and the counterpressure place 1 2 on the other hand, the springs 26 being disposed on the side of the space outside the clutch, which is towards the engine side A.
The other fixing location 27 for the springs 26 is disposed on the clutch carrier plate 3, more specifically, also on the outward side of the clutch, which is towards the engine side A. The fixing location is disposed on a bulge portion 28 in the clutch carrier plate 3, which is directed towards the engine side A, while-as viewed in the peripheral direction and towards the fixing location 25-the portion 28 is followed by a portion 29 which is set back in the axial direction.
The springs 26 are fixed to the clutch carrier plate 3 by way of rivets 30. Disposed in opposing relationship to the head 31 of the rivet 30 is a flat support face 32 on the pressure plate, which serves as a contact face for the rivet 30 in the riveting operation. In that connection, the arrangement may be such that the rivet 30 has a setting head 31 forced thereon, and the head 33 which is on the outward side A of the clutch is formed as a closure head, while the portion 31 which is formed as the setting head is supported against the face 32 during the riveting operation. However, the rivet connection may also be formed in such a way that the head 33 is the setting head, the rivet is passed through the spring 26 and the opening in the clutch carrier plate 3, and the head 31 is formed as the closure head, the face 32 virtually acting as a rivet punch during the riveting operation.
At any event, the spacing between the face 32 and the head 31 is so selected as to ensure a satisfactory disengagement lift motion of the pressure plate 4, even in the new condition of the clutch.
The springs 26 are riveted to the pressure plate by way of a blind rivet connection 34 wherein a rivet element 36 is inserted into a blind bore 35 which is provided with undercut portions (not shown in detail), such as for example a screwthread. The rivet element 36 comprises a hollow body 37 which initially projects beyond the springs 26, with a portion which is shown in broken lines. A spreader element 38 which is larger in diameter than the internal bore in the hollow body is driven into the illustrated position in the hollow body 37, with its tapered portion 39 which is directed towards the friction surface of the pressure plate leading in the driving-in operation, whereby the hollow body 37 is expanded and spread into the undercut pOrtions.
The spreader pin also has, at its end which is remote from the friction surface of the pressure plate 4, a tapering portion 40 which, when the closure head 41 is formed, is virtually covered or enclosed thereby so that the spreader pin 38 which remains in the hollow body is satisfactorily secured in position.
The portion 42 of the clutch carrier plate 3, that portion 42 being adjacent to the fixing region, on the pressure plate side, at the lugs 23,-in the direction in which the plate spring extends to the rivet 30-is a calibrated region and serves as an abutment for the springs 26. The spacing between the abutment region 42 and the oppositely disposed region of the springs 26 is so selected that, although axial movement of the pressure plate 4 to at least approximately the maximum position of wear of the friction linings 10 of the clutch plate 11 is permitted, nonetheless over-stretching of the springs 26 is avoided, when only the pressure plate 4, the diaphragm spring 5 and the clutch carrier plate 3 are assembled.
For the purposes of installing the cupshaped spacer or mounting means 13, and the counterpressure plate 12 connected thereto, in the proper position when assembling those components and the clutch plate 11 on the clutch carrier plate 3, provided in the latter is a centering pin 43 which engages into a centering bore 44, although the centering contour may also be a radially extending slot. The centering contour 44 is provided in a pocket 45, which projects in the axial direction towards the engine, in the region of the edge 14 of the spacer means, wherein the region 45 is in turn provided in the region of the portion 28 in the clutch carrier plate 3.
The clamping pin or the clamping sleeve 43 may be disposed at least approximately in the region of the springs 26, while the springs 26, as shown in broken lines in the lower part of Figure 1, at least partially cover over the pin 43 by a cover portion 46, thereby ensuring that the pin is satisfactorily held in position and cannot be pressed out when fitting the spacing bridging or mounting means 1 3.
Figure 4 shows that the fixing rivet for connecting the springs 26 to the clutch carrier plate 3 and the centering means for the spacer or mounting means 1 3 may also be formed by a common element 47. The element 47 has an abutment shoulder 48, a centering portion 49 and the closure head 50 which is formed on the plate spring side. The centering contour 44 is illustrated in this case in the form of a radial slot which is open outwardly. However, it could also be in the form of a radially elongate slot which terminates before the outside contour of the cover means. That avoids any effects which could occur due to slight radial movement when pressing on the toothed ring.

Claims (21)

1. A friction clutch, in particular for motor vehicles, comprising a clutch carrier plate which can be secured to the crankshaft of an engine, an axially movable pressure plate, a diaphragm spring which is disposed between the pressure plate and the clutch carrier plate and which bears with radially outward regions against the clutch carrier plate and which engages the pressure plate with radially further inwardly disposed regions, wherein torque transmission means are provided between the pressure plate and the clutch carrier plate, a counter pressure plate which can be axially and non-rotatably secured to the clutch carrier plate by way of spacer means, and a clutch plate which is to be disposed between the counter pressure plate and the pressure plate, characterised in that the torque transmission means are provided in the form of leaf springs (26) on the outer space (A), which is towards the engine side, of the clutch (1).
2. A friction clutch according to claim 1 characterised in that the pressure plate (4) is provided with lugs (23) which face axially towards the engine and which extend through the clutch carrier plate (3) through apertures (24) therein.
3. A friction clutch according to claim 1 or claim 2 characterised in that the leaf springs (26) which are provided on the outward side (A) of the clutch are secured to a face (25) of the lugs (23), which faces towards the engine.
4. A friction clutch according to one of claims 1 to 3 characterised in that the axially directed lugs (23) which pass through the clutch carrier plate (3) towards the engine side (A) are disposed at least substantially within the radial extent of the friction linings (10) of the clutch plate (11) and the support for the diaphragm spring (5) on the clutch carrier plate (3) is disposed radially between the lugs (23) and the support (at 9) on the pressure plate (4).
5. A friction clutch according to one of claims 1 to 4 characterised in that the fixing Iccations (27) of the leaf springs (26) on the clutch carrier plate (3) are also on the outward side (A), which is towards the engine side, of the clutch (1).
6. A friction clutch according to one of claims 1 to 5 characterised in that the fixing location (27) of the leaf spring elements (26), which is on the clutch carrier plate side, is disposed on a bulged portion (28), which is formed out towards the engine, in the clutch carrier plate (3), while a bulged portion (29) which is formed in a direction towards the counterpressure plate (12) is formed in the clutch carrier plate (3) in the region of the lugs (27).
7. A friction clutch according to one of claims 1 to 6 characterised in that the region (42) of the clutch carrier plate (3), which region (42) is adjacent to the fixing region (25) of the lugs (23), on the pressure plate side, as viewed in the direction in which the leaf springs extend to the fixing region (27) on the clutch carrier plate side, serves as an abutment (42) for the leaf springs (26).
8. A friction clutch according to claim 7 characterised in that the abutment region (42) is calibrated.
9. A friction clutch in particular according to one of claims 1 to 8 characterised in that a flat face of the pressure plate (4) is disposed in opposite relationship to the fixing rivets (30) for fixing the leaf springs (26) to the clutch carrier plate (3), as a support face (32) for the riveting operation.
1 0. A friction clutch according to claim 9 characterised in that in the new condition and when the clutch is closed, a spacing corresponding at least to the lift motion of the pressure plate (4) is provided between the support face (32) and the rivet head (31) which is towards the support face (32).
11. A friction clutch according to one of claims 1 to 10 characterised in that a centering pin (43) is provided for centering the spacer means (13) or the components connected thereto in the clutch carrier plate (3) in the direct vicinity of the leaf spring fixing location (27).
1 2. A friction clutch according to claim 11 characterised in that the centering pin (43) is at least partially covered by the leaf springs (26) in a radial direction, on the outward side (A), which is towards the engine, of the clutch carrier plate (3).
1 3. A friction clutch according to at least one of the preceding claims characterised in that the rivet (30) for fixing the leaf springs (26) to the clutch carrier plate (3) and a centering pin (43) for centering the spacer means (13) or the component connected thereto are fixed in the same region of the clutch carrier plate (3).
1 4. A friction clutch according to claim 1 3 characterised in that the leaf spring fixing rivet and the centering pin (43) are formed by a common element (47).
1 5. A friction clutch according to one of claims 1 to 14 characterised in that the leaf springs (26) are fixed on the pressure plate side by means of a blind rivet connection (34) made in the lugs (23).
16. A friction clutch in particular according to claim 1 5 characterised in that a hollow rivet element (36) is fitted into a blind bore (35) provided in the lugs (23) and at least a portion of the section, which is in the blind bore (35), of the rivet element (36) is spread radially towards the contours of the blind bore (35).
1 7. A friction clutch according to claim 1 6 characterised in that the blind bore (35) has at least one respective profiling or undercut configuration which increases its diameter and into which the rivet element (36) is plastically deformed by being radially expanded.
1 8. A friction clutch according to claim 1 7 characterised in that the profiling is of a screwthread-like configuration.
1 9. A friction clutch according to one of claims 1 6 to 1 8 characterised in that the spreading effect is produced by driving in a spreader pin (38) which tapers at its end which is towards the friction surface and which remains in the bore in the rivet element (36).
20. A friction clutch according to one of claims 1 6 to 1 9 characterised in that the rivet element is a hollow rivet member with a head formed thereon.
21. A friction clutch according to one of claims 1 6 to 20 characterised in that the spreader pin (38) has a tapering region (40) at its end which is towards the friction surface and the head (41) of the rivet (36) is peened over radially towards said region (40).
GB08407816A 1983-03-25 1984-03-26 Friction clutch Expired GB2137292B (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3311039 1983-03-25
DE19833347913 DE3347913A1 (en) 1983-03-25 1983-05-26 Friction clutch

Publications (3)

Publication Number Publication Date
GB8407816D0 GB8407816D0 (en) 1984-05-02
GB2137292A true GB2137292A (en) 1984-10-03
GB2137292B GB2137292B (en) 1987-04-29

Family

ID=25809447

Family Applications (1)

Application Number Title Priority Date Filing Date
GB08407816A Expired GB2137292B (en) 1983-03-25 1984-03-26 Friction clutch

Country Status (3)

Country Link
DE (1) DE3347913A1 (en)
FR (1) FR2543240B1 (en)
GB (1) GB2137292B (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8479907B2 (en) 2010-01-20 2013-07-09 Volkswagen Ag Clutch unit

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3336158A1 (en) * 1983-10-05 1985-04-18 Fichtel & Sachs Ag, 8720 Schweinfurt Pressure plate for friction clutches
DE4420927B4 (en) * 1993-06-19 2005-12-01 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Torque transfer device
DE19502617C2 (en) * 1995-01-27 1998-09-17 Mannesmann Sachs Ag Dual-mass flywheel with engine-side pressure plate
FR2753502B1 (en) * 1996-09-19 1999-02-12 Valeo CLUTCH WITH REDUCED AXIAL OVERALL FRICTION

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB704437A (en) * 1952-03-17 1954-02-24 Dana Corp Friction clutch with spring supported pressure plate
GB1194430A (en) * 1966-11-18 1970-06-10 Aisin Seiki Clutch Assembly
GB1233996A (en) * 1969-03-26 1971-06-03

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB570735A (en) * 1944-01-24 1945-07-19 Blackburn Aircraft Ltd Improvements in and relating to hollow rivets
GB572082A (en) * 1944-03-06 1945-09-21 Fairey Aviat Co Ltd Improvements in or relating to rivetting
GB640451A (en) * 1946-09-02 1950-07-19 Aviat Developments Ltd Improvements in or relating to tubular fastening devices or bushes
GB642770A (en) * 1947-12-19 1950-09-13 Blackburn Aircraft Ltd A rivet for use in riveting into a blind hole
NL91681C (en) * 1952-09-02
US3167163A (en) * 1962-01-02 1965-01-26 Borg Warner Axially engaging clutch with strut, sheet metal levers, and cover plate
US3221856A (en) * 1963-06-10 1965-12-07 Dana Corp Friction clutch
DE1605919B2 (en) * 1967-11-17 1974-12-19 Aisin Seiki Co. Ltd., Kariya, Aichi (Japan) Friction clutch for vehicles
FR1594908A (en) * 1968-02-07 1970-06-08
DE2042419A1 (en) * 1970-08-27 1972-03-02 Fichtel & Sachs Ag Pressure plate, preferably for large diameter diaphragm spring dry friction clutches
DE2114661A1 (en) * 1971-03-26 1972-10-05 Fichtel & Sachs Ag, 8720 Schweinfurt Disc friction clutch with diaphragm spring and release pin
DE2121919C3 (en) * 1971-05-04 1983-11-24 LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl Friction clutch
DE2302410C3 (en) * 1973-01-18 1981-09-03 Hilti AG, 9494 Schaan Process for the repair of molds and expansion dowels for carrying out the process
FR2282563A1 (en) * 1974-08-23 1976-03-19 Ferodo Sa Stud fixing of sheet materials - with boss on base material deformed on assembly to grip grooved shank
US4013685A (en) * 1975-03-10 1977-03-22 Stauffer Chemical Company Process for the manufacture of n(mercaptomethyl) phthalimide s-(o,o-dimethyl phosphorodithioate
FR2507719B1 (en) * 1981-06-12 1986-08-29 Valeo CLUTCH MECHANISM, ESPECIALLY FOR MOTOR VEHICLES

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB704437A (en) * 1952-03-17 1954-02-24 Dana Corp Friction clutch with spring supported pressure plate
GB1194430A (en) * 1966-11-18 1970-06-10 Aisin Seiki Clutch Assembly
GB1233996A (en) * 1969-03-26 1971-06-03

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8479907B2 (en) 2010-01-20 2013-07-09 Volkswagen Ag Clutch unit

Also Published As

Publication number Publication date
FR2543240B1 (en) 1988-07-01
GB8407816D0 (en) 1984-05-02
FR2543240A1 (en) 1984-09-28
DE3347913C2 (en) 1992-05-21
DE3347913A1 (en) 1985-06-27
GB2137292B (en) 1987-04-29

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