GB2103758A - Clutch disk assembly with rotational damping construction including heat dissipating metal plate - Google Patents
Clutch disk assembly with rotational damping construction including heat dissipating metal plate Download PDFInfo
- Publication number
- GB2103758A GB2103758A GB08218928A GB8218928A GB2103758A GB 2103758 A GB2103758 A GB 2103758A GB 08218928 A GB08218928 A GB 08218928A GB 8218928 A GB8218928 A GB 8218928A GB 2103758 A GB2103758 A GB 2103758A
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- Prior art keywords
- clutch disk
- plastic
- flange
- clutch
- hub
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/129—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by friction-damping means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
A clutch disk assembly includes a hub 1 with an intermediate integrally formed flange 2. A plastic bush 13 with radially larger and radially smaller portions is fitted rotatably over one end of the hub, with its radially larger portion towards the flange. A main clutch disk plate 3 is fitted over the radially smaller portion of the bush, abutting against the radially larger portion. An auxiliary clutch disk plate 4 is fitted over the other end of the hub, and is fixed both in the axial and radial directions to the main plate. The combination of these plates is coupled to the flange with a certain amount of sprung rotational play being available therebetween, and is also biased in the axial direction which presses the main plate and the bush toward the flange. A means is provided frictionally to damp rotational movement between the combination of the plates and the flange. A plastic friction ring 14 is provided between the radially larger portion of the bush and the flange with a metallic intermediate ring 15 being provided between the radially larger portion of the bush and the plastic friction ring. <IMAGE>
Description
SPECIFICATION
Clutch disk assembly with rotational damping construction including heat dissipating metal plate
The present invention relates to a clutch disk assembly for a friction type clutch for an automotive vehicle, and, more particularly, relates to a clutch disk assembly for a friction type clutch for a vehicle, which incorporates a rotational damping construction which is particularly durable.
A clutch assembly such as a manually operated clutch assembly for an automotive vehicle generally incorporates a clutch disk assembly and a clutch pressure plate assembly. One assembly of this clutch disk assembly and this clutch pressure plate assembly is rotationally coupled, typically by a hub member thereof, to the crankshaft of an internal combustion engine of the vehicle, and the other of said assemblies is rotationally coupled, again typically by a hub member thereof, to a power input shaft of a gear transmission mechanism of the vehicle. Arrangements are provided for selectively either biasing one assembly of the clutch disk assembly and the clutch pressure plate assembly towards the other of said assemblies or away from the other of said assemblies.Thus, when the clutch disk assembly and the clutch pressure plate assembly are biased together, then the clutch pressure plate assembly presses against a lining or linings fixed typically on the outer peripheral part of the clutch plate assembly, so that the clutch disk assembly and the clutch pressure plate assembly are rotationally engaged together, and in this state the aforesaid crankshaft of the internal combustion engine of the vehicle is rotationally coupled to said power input shaft of-said gear transmission mechanism, thus driving said gear transmission mechanism and driving said vehicle along the road; but, on the other hand, when the clutch disk assembly and the clutch pressure plate assembly are biased dway from one another, then the clutch pressure plate assembly moves away from said lining or linings fixed to the clutch plate assembly, so that the clutch disk assembly and the clutch pressure plate assembly are rotationally disengaged from one another, and in this state the aforesaid crankshaft of the internal combustion engine of the vehicle is not substantially rotationally coupled to said power input shaft of said gear transmission mechanism, thus not providing input power to said gear transmission mechanism and not driving said vehicle along the road.
Now, in the use of a vehicle incorporating such a per se well known type of clutch assembly, as a matter of course drivability of the vehicle is very important. The prevention of so called clutch snatching, and the cushioning of torque shock transmitted along the drive train of the vehicle, especially when changing between speed stages of the gear transmission mechanism and thus disengaging and engaging the clutch assembly as explained above, is important with regard to maintaining the drivability of the vehicle at an acceptable level, and also with regard to ensuring a long operating life for the clutch assembly and also for the other parts of the drive train of the vehicle such as the gear transmission mechanism.
One way which is effective, and has been practiced, for reducing such clutch snatching and for cushioning such torque shock has been for the clutch disk assembly to be formed with a certain amount of sprung rotational play therein between its outer peripheral portion to which said lining or linings are fixed and its hub portion which is rotationally coupled to said crankshaft of said internal combustion engine of the vehicle or to the power input shaft of the gearbox. In more detail, it is conventional and has been practiced for the clutch disk assembly to be formed with a hub and with a plate assembly, which is rotationally mounted to the hub, and which is rotationally coupled to the hub via some assembly such as a plurality of springs.In such a construction, the plate assembly can rotate to a certain limited degree with respect to the hub, but the more said plate assembly moves relative to said hub away from a preferred relative position the greater becomes the force due to said springs or the like which tends to restore the mutual position of said plate assembly and said hub to said preferred relative position. Thus this limited amount of sprung rotational play between the plate assembly -- which is conventionally formed as a pair of plates rigidly coupled together on either side of a flange formed integrally with the hub member - and the hub member, is capable of cushioning such torque shock which is being transmitted along the drive train of the vehicle, and of preventing the occurrence of clutch snatch.
Thus the drivability of the vehicle is maintained.
In such a construction, furthermore, it is known and conventional to mount the plate assembly on the hub member - in more detail, on a projecting part thereof which extends on one side of said flange thereof - by way of a plastic bush, which is formed of a fairly hard plastic substance, in view of the high forces which it must sustain.The use of such a plastic bush means that metal to metal contact between the plate assembly and the hub member can be avoided, and, by suitably choosing the plastic material concerned, a fairly low coefficient of friction can be attained, and thus the plate assembly and the plastic bush which typically is set in a central hole of a main plate member of said plate assembly can rotate smoothly, when required to do so according to the above explained torque cushioning action, on said projecting part of said hub member, by the plastic bush rotating on said projecting part with a plastic to metal contact.
Further, during the operation of such a vehicle, even when not changing between speed stages of the gear transmission mechanism and thus disengaging and engaging the clutch assembly, there is a danger of vibrations of various kinds occurring in the drive train of the vehicle -- these vibrations may be particularly troublesome in the case of resonant twisting vibration modes and there is also a danger of peculiar noises arising in the drive train of the vehicle, as for example noises caused by the gears of the gear transmission mechanism. These problems can be aggravated if the gears of the gear transmission mechanism operate with a certain degree of backlash.One way which is effective, and has been practiced, for reducing the incidence of such vibrations, and for quietening down said noise, has been for the aforementioned sprung rotational play between the clutch plate assembly and the clutch disk hub to be also rotationally damped; in other words, a rotational damper assembly is provided between said clutch plate assembly and said clutch disk hub. Various constructions have been conceived of, and used, for such a rotational damper assembly; and a typical one is a kind in which a friction member such as an annulus, rotationally coupled to the clutch plate assembly, is pressed against a side of the aforementioned flange formed integrally with the hub member.In such a construction, the frictional force between said friction annul us and said flange provides a degree of rotational damping between the clutch plate assembly and the hub, and accordingly vibrations and noise which would otherwise occur in the drive train of the vehicle are absorbed by this damping effect.
A problem which has arisen with this kind of construction is as follows. The biasing of the friction annulus against the flange which is formed integrally with the hub member is typically required to be quite strong, in order to provide a good frictional force therebetween adequate for providing a sufficient rotational damping effect, and the biasing means such as a spring (which may be a ring spring) which performs this biasing typically bears against some part of the clutch plate assembly. This tends to bias the clutch plate assembly as a whole in a certain direction relative to the hub and the flange formed integrally therewith, and the question arises as to how this biasing is to be borne.In a typical construction, this biasing tends to push one side of the aforesaid plastic bush quite hard against one side of the flange such as the opposite side of the flange to the side which contacts the friction annulus, and when the plastic bush rotates relative to the hub and the flange the problem has arisen that this rubbing contact of the side of the bush against the flange wears away the bush to a great extent, since the plastic material of which the plastic bush is made is not designed to be extremely effective with regard to wear resistance when pressed against a cooperating metal surface, but rather is designed to be strong in order to support the load put upon said plastic bush by the clutch plate assembly being mounted thereon.This wearing away of the plastic bush means that the rotational damping effect provided by the aforesaid friction annulus becomes deteriorated, since the pressure exerted by the aforesaid biasing means for the friction annulus such as a ring spring is not effectively and uniformly backed up. Accordingly, the operation of the vehicle may become attended with high levels of noise and vibration occurring in the drive train thereof.
A way which has been previously conceived of and practiced for curing this problem has been to provide, between the face of the plastic bush which faces towards said flange and the face of said flange which faces towards said plastic bush, an annular intermediate plastic member formed of tetrafluorethylene resin or the like, which is a substance which has a constant and fairly low coefficient of friction when rubbed against either metal or plastic such as the plastic of the plastic bush, and which is resistant to pressure.
Now, this expedient has been successful as far as achieving its object of preventing wear on the plastic bush and of properly backing up the pressure of the biasing means for the friction annulus is concerned, but the following problem has occurred. Because as explained above the pressing force between the face of the plastic bush which faces towards the flange and the aforesaid annular intermediate plastic member is quite high, therefore, although the coefficient of friction between the material of the plastic bush and the material of the annular intermediate plastic member is very low, nevertheless according to this quite high pressure between these members an amount cf heat which is not negligible is generated between them, when they move with respect to one another according to the above described torque shock cushioning effect of the construction. The problem is that, because the coefficient of thermal conduction of the material of the plastic bush is typically very low, and the coefficient of thermal conduction of the material of the annular intermediate plastic member is also typically very low, this heat is trapped between these members, and cannot easily escape.
Accordingly, even though in absolute terms the amount of this heat may not be so very great, over a period of time during intensive use of the vehicle this heat can build up between the annular intermediate plastic member and the plastic bush and can create a high temperature between them.
This high temperature can have the effect of softening or even fusing or melting the plastic material of either the annular intermediate plastic member or the plastic bush, and in such a case the durability of the construction is severely deteriorated. This problem of poor dissipation of the frictional heat generated between the annular intermediate plastic member and the plastic bush, by the way, does not substantially occur in the case of the annular intermediate plastic member and the flange integrally formed on the hub member, because the material of the flange is metal and accordingly quickly conducts away the frictionally generated heat.
Accordingly, it is the primary object of the present invention to provide a clutch disk assembly, of the above explained sort incorporating a plastic bush which supports a clutch plate assembly and also incorporating an annular intermediate plastic member between such a flange and said plastic bush, in which the abovementioned problem of buildup of heat in between such a plastic bush and such an annular intermediate plastic member is overcome.
It is a further object of the present invention to provide a clutch disk assembly in which there is no likelihood of fusing caused by high temperature of the material of such a plastic bush or of such an annular intermediate plastic member.
It is a further object of the present invention to provide a clutch disk assembly in which there is no likelihood of melting caused by high temperature of the material of such a plastic bush or of such an annular intermediate plastic member.
it is a further object of the present invention to provide a clutch disk assembly in which there is no likelihood of deformation caused by high temperature of the material of such a plastic bush or of such an annular intermediate plastic member.
It is a further object of the present invention to provide such a clutch disk assembly, in which the frictional heat inevitably produced between such a plastic bush and such an annular intermediate plastic member does not build up to such an extent as to cause a high temperature to be generated in the region between these two members.
It is a further object of the present invention to provide such a clutch disk assembly, in which the frictional heat inevitably produced between such a plastic bush and such an annular intermediate plastic member is well dissipated.
It is a further object of the present invention to provide such a clutch disk assembly, in which such a plastic bush and such an annular intermediate plastic member are both well cooled down.
It is a further object of the present invention to provide such a clutch disk assembly, in which such a plastic bush and such an annular intermediate plastic member are both well cooled down, in particular, by the process of heat conduction.
It is a further object of the present invention to provide such a clutch disk assembly, in which such a plastic bush and such an annular intermediate plastic member are both well cooled down, in particular, by the process of heat convection.
It is a further object of the present invention to provide such a clutch disk assembly, in which such a plastic bush and such an annular intermediate plastic member are both well cooled down, in particular, by the process of heat radiation.
It is a further object of the present invention to provide such a clutch disk assembly, in which such a clutch plate assembly may be supported reliably by such a plastic bush with regard to its position on said hub member, without any durability problems being caused.
It is a further object of the present invention to provide such a clutch disk assembly, in which a stable and durable backing is provided for the pressure of such an annular friction member against such a flange formed integrally with the hub member, in order to make available good and durable rotational damping.
It is a further object of the present invention to provide such a clutch disk assembly, in the use of which the life of the clutch assembly as a whole is made acceptably long.
It is a further object of the present invention to provide such a clutch disk assembly, in the use of which the life of the parts of the drive train of the vehicle incorporating said clutch disk assembly as a whole is made acceptably long.
It is a further object of the present invention to provide such a clutch disk assembly, which in itself has good durability.
It is yet a further object of the present invention to provide such a clutch disk assembly, which suppresses noise in the drive train of the vehicle incorporating said clutch disk assembly, especially gear noise caused by gears in a gear transmission mechanism used therewith.
It is yet a further object of the present invention to provide such a clutch disk assembly, which suppresses vibration in the drive train of the vehicle incorporating said clutch disk assembly.
It is yet a further object of the present invention to provide such a clutch disk assembly, which cushions transmission torque shock in the drive train of the vehicle incorporating said clutch disk assembly, especially transmission torque shock caused by shifting of speed shift stage of a gear transmission mechanism used therewith.
It is yet a further object of the present invention to provide such a clutch disk assembly, which provides good rotational cushioning when the clutch of the vehicle incorporating said clutch disk assembly is engaged or is disengaged.
It is yet a further object of the present invention to provide such a clutch disk assembly, which provides good rotational damping when the clutch of the vehicle incorporating said clutch disk assembly is engaged or is disengaged.
It is yet a further object of the present invention to provide such a clutch disk assembly, which prevents snatching of the clutch of the vehicle incorporating said clutch disk assembly.
It is yet a further object of the present invention to provide such a clutch disk assembly, which provides good drivability for the vehicle incorporating said clutch disk assembly.
According to the present invention, these and other objects are accomplished by a clutch disk assembly, comprising: (a) a clutch disk hub with an integrally formed clutch disk flange located at an intermediate position therealong; (b) a plastic hub bush fitted rotatably over the part of said clutch disk hub on a first side of said clutch disk flange, formed with a radially smaller portion on its side remote from said clutch disk flange and a radially larger portion on its side towards said clutch disk flange; (c) a main disk plate formed with a central hole, said main disk plate being mounted via its central hole over said radially smaller portion of said plastic hub bush and being abutted against the side of said radially larger portion of said plastic hub bush which is remote from said clutch disk flange; (d) an auxiliary disk plate formed with a central hole, said auxiliary disk plate being fitted via its central hole over the part of said clutch disk hub on the side of said clutch disk flange opposite to said first side thereof; (e) means for fixedly coupling said main disk plate and said auxiliary disk plate together both with regard to relative axial movement thereof and with regard to relative rotational movement thereof;; (f) means for coupling said coupled combination of said main disk plate and said auxiliary disk plate to said clutch disk flange with a certain amount of rotational play being available therebetween, and for, when said rotational play is non zero in either rotational direction, exerting a spring force between said coupled combination of said main disk plate and said auxiliary disk plate and said clutch disk flange in the appropriate direction to cancel such rotational play; (g) means for biasing said coupled combination of said main disk plate and said auxiliary disk plate in the axial direction relative to said clutch disk hub which presses said main disk plate towards said clutch disk flange and which presses said plastic hub bush towards said clutch disk flange via said abutting contact of said main disk plate with said side of said radially larger portion of said plastic hub bush which is
remote from said clutch disk flange; (h) means for, when said coupled combination of said main disk plate and said auxiliary disk plate moves relative to the combination of said clutch disk hub and said clutch disk flange, exerting a rotational frictional damping force between said coupled combination of said main disk plate and said auxiliary disk plate and said combination of said clutch disk hub and said clutch disk flange; (i) a plastic friction annulus located between said side of said radially larger portion of said plastic hub bush which faces towards said clutch disk flange and the side of said clutch disk flange which faces towards said
plastic hub bush; and (j) a metallic intermediate annulus located between said side of said radially
larger portion of said plastic hub bush which faces towards said clutch disk flange and the side of said plastic friction annulus which faces towards said plastic hub bush, and directly abutted against said side of said plastic friction annulus which faces towards said plastic hub bush.
According to such a structure, because said side of said plastic friction annulus which faces towards said plastic hub bush is contacted against, not said plastic hub bush as was the case in the prior art, but said metallic intermediate annulus, and because said metallic intermediate annulus is formed of metal which as a matter of course has a fairly high coefficient of heat conduction, thereby the heat generated when said plastic friction annulus rubs against said metallic intermediate annulus is quickly conducted through the metallic material of said metallic intermediate annulus to be transferred both to the outside atmosphere (in fact via the radially outermost part of said metallic intermediate annulus) and to the clutch disk hub (in fact via the radially innermost part of said metallic intermediate annulus).
Thereby the cooling of the parts of the construction in which friction is liable to generate heat is much improved, and accordingly this heat is not allowed to build up and create such a high temperature as could lead to melting or fusing of the plastic friction annulus and/or the plastic hub bush, or to deformation of any of the various parts of the construction.Accordingly, there is provided a good backing up for the action of the means for biasing said coupled combination of said main disk plate and said auxiliary disk plate in the axial direction relative to said clutch disk hub which presses said main disk plate towards said clutch disk flange and which presses said plastic hub bush towards said clutch disk flange, which is in the general form of the construction very important for ensuring good action of the means for exerting a rotational frictional damping force between said coupled combination of said main disk plate and said auxiliary disk plate and the combination of said clutch disk hub and said clutch disk flange.According to this construction, therefore, the durability of the clutch disk assembly during use is promoted, and also a good function of prevention of clutch snatch during use of the vehicle incorporating the clutch disk assembly is available, by good rotational damping action when the clutch is engaged or is disengaged being provided. Further, noise such as noise produced by the gears of a gear transmission mechanism used with this clutch disk is quietened down, and also vibration in the vehicle drive train as a whole is suppressed.
Transmission torque shock, as for example is inevitably produced when the transmission is shifted between its speed stages, is also cushioned. Thus the drivability of the vehicle incorporating this clutch disk assembly is advantageously promoted.
Further, according to a particular aspect of the present invention, these and other objects are
more particularly and concretely accomplished by either of the constructions detailed above, wherein said plastic hub bush, said plastic friction annulus, and said metallic intermediate annulus are all of substantially the same outer radius.
According to such a structure, the sandwiched combination of said metallic intermediate annulus or metallic intermediate annuli, and of said plastic friction annulus or plastic friction annuli, presents a compact shape, which can be important in certain applications.
Further, according to an alternative particular aspect of the present invention, these and other objects are more particularly and concretely accomplished by either of the alternative first two constructions detailed above, wherein said metallic intermediate annulus is of substantially larger outer radius than said plastic friction annulus, and is also of substantially larger outer radius than said radially larger part of said plastic hub bush.
According to such a structure, the outer peripheral portion or portions of the metallic intermediate annulus or the metallic intermediate annuli projects out from past the outer peripheral portion or portions of the plastic friction annulus or the plastic friction annuli and out from past the outer peripheral portion of said radially large portion of said plastic hub bush, and accordingly is provided with much better cooling both by convection to the atmosphere and also by radiation.Thereby the heat generated when said plastic friction annulus or plastic friction annuli rub against said metallic intermediate annulus or metallic intermediate annuli is more quickly conducted through the metallic material of said metallic intermediate annulus or metallic intermediate annuli to be transferred to the outside atmosphere via the radially outermost parts of said metallic intermediate annulus or metallic intermediate annuli.
Further, according to an alternative particular aspect of the present invention, there and other objects are more particularly and concretely accomplished by either of the alternative first two constructions detailed above, wherein the other side of said metallic intermediate annulus from the side thereof which is directly abutted against the side of said plastic friction annulus which faces towards said plastic hub bush is directly abutted against the side of said plastic hub bush which faces towards said clutch disk flange.
According to such a structure, in fact, all the sliding contacts performed between the plastic friction annulus or plastic friction annuli, the metallic intermediate annulus or metallic intermediate annuli, and the plastic hub bush are metal to plastic contacts, and none of them are plastic to plastic contacts. The advantage of this is that, as mentioned above, thereby heat generated at each of these contact surfaces is quickly conducted away because of the high coefficient of thermal conductivity of the metallic intermediate annulus or metallic intermediate annuli, and does not build up to create an unacceptably high temperature.
The present invention will now be shown and described with reference to several preferred embodiments thereof, and with reference to the illustrative drawings. It should be clearly understood, however, that the description of the embodiments, and the drawings, are all of them given purely for the purposes of explanation and exemplification only, and are none of them intended to be limitative of the scope of the present invention in any way, since the scope of the present invention is to be defined solely by the legitimate and proper scope of the appended claims.In the drawings:
Fig. 1 is a longitudinal sectional view taken through a clutch disk assembly which is a first preferred embodiment of the clutch disk assembly according to the present invention, the plane of this section including the central rotational axis of said clutch disk assembly; and
Fig. 2 is a longitudinal sectional view similar to
Fig. 1, but drawn at a larger scale than Fig. 1, showing the essential parts of a second preferred embodiment of the present invention which is a slight modification of said first preferred embodiment shown in Fig. 1.
The present invention will now be described with reference to several preferred embodiments thereof, and with reference to the appended drawings. Fig. 1 is a sectional view of a clutch disk assembly which is the first preferred embodiment of the clutch disk assembly according to the present invention, taken along the central rotational axis thereof, i.e. the axis of symmetry thereof. The reference numeral 1 denotes the clutch disk hub of this clutch disk assembly, said clutch disk hub 1 being formed generally as a hollow cylinder, and at an axially central part of this cylindrical clutch disk hub 1 there is formed integrally therewith a clutch disk flange 2 which is of a generally annular form and which extends in a plane perpendicular to the central axis of the clutch disk assembly.
On opposite sides of the clutch disk flange 2 there are disposed a main disk plate 3 and an auxiliary disk plate 4, each of which is formed as a generally annular element with a central hole, disposed around an end portion of the clutch disk hub 1 with said end of the clutch disk hub 1 protruding through said central hole. Each of the main disk plate 3 and the auxiliary disk plate 4 is both axially and rotationally slidably mounted on said protruding end of the clutch disk hub 1 so as to be able to turn with respect thereto about the central rotational axis of the clutch disk assembly, and also so as to be able to slide axially with respect thereto along said central rotational axis.
However, the main disk plate 3 and the auxiliary disk plate 4 are fixed together both in the axial direction and with regard to mutual rotation with respect to the central rotational axis of the clutch disk assembly by a bracing construction which will now be explained.
A plurality of fixing pins 5 which extend in the direction generally parallel to said central rotational axis of the clutch disk assembly are provided as extending between said main disk plate 3 and said auxiliary disk plate 4, each of these fixing pins 5 being fixed at its one end to the main disk plate 3 and at its other end to the auxiliary disk plate 4. in fact, as may be understood from the figure, the outer diameter of the auxiliary disk plate 4 is substantially less than the outer diameter of the main disk plate 3, and each of the fixing pins 5, only one of which can be seen in Fig. 1 but which in fact are provided in plurality, extends between a part of the auxiliary disk plate 4 which is substantially at its outer peripheral portion to a part of the main disk plate 3 which is some substantial distance radially inward of its outer peripheral portion.For each of the fixing pins 5 there is cut an opening or gap 2a through the outer peripheral portion of the clutch disk flange 2 to allow said fixing pin 5 to pass therethrough, because in fact the outer diameter of the clutch disk flange 2, in the shown first preferred embodiment of the clutch disk assembly according to the present invention, is substantially the same as the outer diameter of the auxiliary disk plate 4.Thus, the main disk plate 3 is braced and fixed with respect to the auxiliary disk plate 4 both with respect to movement in the axial direction of the clutch disk assembly and with respect to rotation around the central rotational axis of said clutch disk assembly, but the combination of the main disk plate 3 and the auxiliary disk plate 4 is able to rotate with respect to the clutch disk hub 1 around said central rotational axis of the clutch disk assembly and is also free to move (as far as the above discussed arrangements are concerned) in the axial direction of the clutch disk assembly.
In the rotational sense around said central rotation axis of the clutch disk assembly, the combination of the main disk plate 3 and the auxiliary disk plate 4 is coupled to the clutch disk flange 2 and thus to the clutch disk hub 1 by an arrangement which will now be described. A plurality of compression coil springs 8, only one of which can be seen in the figure but which are provided in plurality, are provided as located between the main disk plate 3 and the auxiliary disk plate 4 and extending around the circumferential direction thereof, i.e. substantially skew perpendicular to the central axis of the clutch disk assembly.The side portions of these compression coil springs 8 are received in circumferentially extending slots 20 and 21 which are cut in mutually opposing positions in the main disk plate 3 and in the auxiliary disk plate 4, respectively, said slots being formed with lips 22, 23 and 24, 25 along their long edges which are angled towards the outside (i.e. away from the clutch disk flange 2), in order snugly to receive said compression coil springs 8, without the edges of said slots grating on the coils of said compression coil springs 8 as said compression coil springs 8 are compressed and are expanded.
Further, slots such as 26 (only one of which is shown in Fig. 1) are cut in the clutch disk flange 2 so as to receive said compression coil springs 8, the central axes of said compression coil springs 8 lying in said slots, substantially in the central plane of said clutch disk flange 2. Thus, when the combination of the main disk plate 3 and the auxiliary disk plate 4 rotates to a certain small extent with respect to the clutch disk hub 1 and the clutch disk flange 2 in a certain one rotational direction, which typically occurs when the clutch incorporating this clutch disk assembly is engaged or disengaged, then the end of each of the compression coil springs 8 in that one rotational direction abuts against the end of the corresponding slot in the clutch disk flange 2 in that one rotational direction, while the end of each of the compression coil springs 8 in the other rotational direction abuts against the ends of the corresponding slots in the main disk plate 3 and in the auxiliary disk plate 4 in the other rotational direction. And, when said combination of the main disk plate 3 and the auxiliary disk plate 4 rotates further with respect to the clutch disk hub 1 and the clutch disk flange 2 in said certain one rotational direction, then the compression coil springs 8 are progressively compressed, so as to provide a force in the opposite rotational direction to said certain one rotational direction on said combination of the main disk plate 3 and the auxiliary disk plate 4 so as to stop said combination rotating further in said certain one rotational relative to the clutch disk flange and the clutch disk hub.Similarly, with respect to rotation of the combination of the main disk plate 3 and the auxiliary disk plate 4 with respect to the clutch disk hub 1 and the clutch disk flange 2 in the other rotational direction, which again may typically occur when the clutch incorporating this clutch disk assembly is engaged or disengaged, when this has occurred to a slight extent then the end of each of the compression coil springs 8 in that other rotational direction abuts against the end of the corresponding slot in the clutch disk flange 2 in that other rotational direction, while the end of each of the compression coil springs 8 in said certain one rotational direction abuts against the ends of the corresponding slots in the main disk plate 3 and in the auxiliary disk plate 4 in said certain one rotational direction.And, when said combination of the main disk plate 3 and the auxiliary disk plate 4 rotates further with respect to the clutch disk hub 1 and the clutch disk flange 2 in said other rotational direction, then the compression coil springs 8 are progressively compressed, so as to provide a force in said certain one rotational direction on said combination of the main disk plate 3 and the auxiliary disk plate 4 so as to stop said combination rotating further in said other rotational direction relative to the clutch disk flange and the clutch disk hub. Thus, this arrangement effectively provides a rotational coupling between the combination of the main disk plate 3 and the auxiliary disk plate 4 and the combination of clutch disk hub 1 and the clutch disk flange 2 with a certain amount of sprung rotational play therebetween.
To the outer circumference of the auxiliary disk plate 4 there are fixed the inner ends of a plurality of plate springs 6, and each side of the outer end of each of these plate springs 6 is fitted with a clutch facing 7. This clutch facing 7 is for engaging, in a per se well known way, with a clutch pressure plate not shown in the figures: this action will not be further discussed in this specification because it is not directly relevant to the present invention and is in any case conventional in itself.
The present invention is particularly related to the arrangements at the portion of the construction where the main disk plate 3 and the auxiliary disk plate 4 are slidably mounted on the clutch disk hub 1 on either side of the clutch disk flange 2. These arrangements are shown in longitudinal section in Fig. 1.The purpose of this construction is to rotatably mount the coupled combination of the main disk plate 3 and the auxiliary disk plate 4 to the clutch disk hub 1 and the clutch disk flange 2 in such a way that said coupled combination is substantially fixed with respect to the clutch disk hub 1 and the clutch disk flange 2 in the axial direction, along the central rotational axis of the clutch disk assembly, and so that said coupled combination is rotatable with respect to the clutch disk hub 1 and the clutch disk flange 2 around said central rotational axis with a certain amount of damping of the mutual motion therebetween being provided.This rotational damping is very important for preventing snatching of the clutch when it is engaged or disengaged, and also for suppressing vibration of the drive train of the vehicle during use, as well as for suppressing noises due to the gears of the gear transmission mechanism incorporated therewith, or the like, and for cushioning transmission torque shock, as for example during shifting between speed stages of said transmission.
First, on the right hand side of the clutch disk flange 2 in the figures, between the clutch disk flange 2 and the auxiliary disk plate 4, there is interposed an annulus formed of friction material, designated in the figures by the reference numeral 9. This friction material may be the same sort of friction material as is used for the clutch facings 7, and has the property of having a high coefficient of friction when it is in rubbing contact with metal.
The side of this friction material annulus 9 which faces away from the clutch disk flange 2 and towards the auxiliary disk plate 4 is securely bonded to a metallic backing annulus 1 which is provided with protruding metal claws 11 a, only one which can be seen in the figures but which in fact are provided in plurality, and each of which enters into and is engaged into a corresponding cut away portion 4a formed in the circumferentially inner portion of the auxiliary disk plate 4. By this arrangement, the metallic backing annulus 11 and'the friction material annulus 9 are rotationally fixedly engaged to the auxiliary disk plate 4 and therefore also to the main disk plate 3.
A ring spring 10 is provided between the metallic backing annulus 11 and the auxiliary disk plate 4 and axialiy biases the metallic backing annulus 11 and the friction material annulus 9 which is securely attached thereto in the direction of the clutch disk flange 2, away from the auxiliary disk plate 4. Over the face of said clutch disk flange 2 which faces the side of said friction material annulus 9 which is thus biased theretowards, there is fitted a metallic facing friction annulus 12, which is formed of a metal whose coefficient of friction when rubbed against the friction material of the friction material annulus 9 is especially high, in order to increase the amount of rotational damping between the combination of the main disk plate 3 and the auxiliary disk plate 4 and the clutch disk hub 1 and the clutch disk flange 2, as will be explained hereinafter.Again, this metallic facing friction annulus 1 2 is provided with projecting claws 1 2a, only one of which can be seen in the figures but which in fact are provided in plurality, each of which enters into and is engaged into a corresponding cut away portion
1 2b formed in the circumferentially inner portion of the clutch disk flange 2. It should be noted that the inner circumferential edge of the auxiliary disk plate defines a circle whose radius is a little larger than the outer radius of the portion of the clutch disk hub 1 over which it fits, so that in fact the auxiliary disk plate 4 is not actually in contact with the clutch disk hub 1 at all, and metal to metal contact in this area does not occur.
Now, on the left hand side of the clutch disk flange 2 in the figures, between the clutch disk flange 2 and the main disk plate 3, there are interposed, in order as proceeding from the right to left of the figures, i.e. from the clutch disk flange 2 towards the main disk plate 3: an annul us formed of a stable plastic resin, for instance formed of tetrafluorethylene resin, designated in the figures by the reference numeral 14; an annulus formed of metal, designated in the figures by the reference numeral 15, which in this first preferred embodiment of the present invention has the same outer radius as the plastic friction annulus 14; and a plastic hub bush 13.The plastic friction annulus 14 and the metallic intermediate annulus 1 5 are each formed as a simple flat annulus which fits snugly and rotatably over the projecting portion of the clutch disk hub 1 which passes through it, but on the other hand the plastic hub bush 13 is formed with a main cylindrical portion 1 3c whose central hole fits snugly and rotatably over the projecting portion of the clutch disk hub 1 which passes through it, and with a flange or shoulder portion 1 3b which extends radially outwards from the right hand portion of said main cylindrical portion of said plastic hub bush 13 in the figures.The inner circumferential edge of the central hole through the main disk plate 3 fits snugly but not particularly rotatably over said main cylindrical portion of said plastic hub bush 13, restingly abutting against the leftwardly facing (in the figures) face of said flange or shoulder portion thereof in order to derive positional stability. The rightwardly facing (in the figures) face of said plastic hub bush 13 which abuts against the metallic intermediate annulus 1 5 is denoted by the reference numeral 1 3a in the figures.
Thus, by the biasing action of the ring spring 10, which is supported by the auxiliary disk plate 4 which reacts against the main disk plate 3 in the axial direction, the multi layered annular sandwich comprising, in order from the left to the right of the figures, the flange or shoulder portion 1 3b of the plastic hub bush 13, the metallic intermediate annulus 15, the plastic friction annulus 14, the clutch disk flange 2, the metallic facing friction annulus 12, the friction material annulus 9, and the metallic backing annulus 11, is kept squeezed together; and, in particular, the main disk plate 3 is kept biased to its extreme possible position in the rightwards direction in the figure with respect to the clutch disk flange 2, so that the combination of the main disk plate 3 and the auxiliary disk plate 4 has substantially no freedom of movement in the axial direction of the clutch disk assembly with respect to the clutch disk hub 1 and the clutch disk flange 2.When the combination of the main disk plate 3 and the auxiliary disk plate 4 rotates around the central rotational axis of the clutch disk assembly with respect to the clutch disk hub 1 and the clutch disk flange 2, of course within the limits dictated by the above explained action of the compression coil springs 8 which act to provide a force which biases against any such mutual angular movement: the main disk plate 3 remains substantially rotationally fixed with respect to the plastic hub bush 13; the metallic facing friction annulus 12 of course remains substantially rotationally fixed with respect to the clutch disk hub 1 and the clutch disk flange 2; and the friction material annulus 9, the metallic backing annulus 11, and the ring spring 10 of course remain substantially rotationally fixed with respect to the auxiliary disk plate 4 and the main disk plate 3; but on the other hand: the inner cylindrical surface of the hole through the plastic hub bush 1 3 slidingly rotates on the outer surface of the part of the clutch disk hub 1 which passes therethrough, this sliding rotational movement being designed to occur with as little friction as possible; the face of the friction material annulus 9 which is in contact with the outer face of the metallic facing friction annulus 12 rubbingly slides thereagainst with a considerable frictional force, the magnitude of this frictional force being determined by the amount of pressure exerted by the ring spring 10 and determining the amount of rotational damping action that is provided between the combination of the main disk plate 3 and the auxiliary disk plate 4 and the clutch disk hub 1 and the clutch disk flange 2; and slippage occurs between the mutually contacting faces of the plastic hub bush 13 and the metallic intermediate annulus 15, between the mutually contacting faces of the metallic intermediate annulus 1 5 and the plastic friction annulus 14, and between the mutually contacting faces of the plastic friction annulus 14 and the clutch disk flange 2, the slippages along these three pairs of annular plane faces of these members occurring without particularly large friction between the members concerned, although of course a certain amount of such friction will inevitably occur.
Now, considering the operation of a prior art type clutch disk assembly of the sort described above, said prior art clutch disk assembly being similar to the clutch disk assembly according to the shown first preferred embodiment of the present invention except not including any metallic plate such as the metallic intermediate annul us 15, it should be understood that, in order to provide a reasonable amount of rotational damping between the combination of the main disk plate 3 and the auxiliary disk plate 4 and the combination of the clutch disk hub 1 and the clutch disk flange 2, the biasing force of the ring spring 10 is required to be quite considerable, in order to produce a considerable biasing force to bias the friction material annulus 9 towards the clutch disk flange 2.Thus the force which squeezes together the whole annular combination sandwich of parts detailed above is required to be quite considerable. Because of this, as has been stated above with reference to the prior art, it has been previously conceived of to provide such a plastic friction annulus as the plastic friction annulus 14, in order to avoid direct rubbing contact between the plastic hub bush 13 and the clutch disk flange 2 which would quickly wear away the material of the plastic hub bush 13 which is typically a rather hard sort of resin plastic.
However, although as mentioned above it is a design objective for the creator of such a prior art type clutch disk assembly to minimize friction between the plastic friction annulus 14 and the plastic hub bush 13, such friction cannot be completely eliminated, and since the compressive load between these members, for the reasons stated above, must be quite large, therefore quite a considerable amount of heat is generated at their mutually rubbing annular surfaces.By the way, in this prior art, no substantial problem exists with regard to the heat generated by the rubbing contact of the plastic friction annulus 14 on the face of the clutch disk flange 2 which said plastic friction annulus 14 contacts, because the material of the clutch disk flange 2 is metal which has a high coefficient of thermal conduction, and thus the entire mass of the clutch disk flange 2 and the clutch disk hub 1 formed integrally therewith functions as a heat sink.But, with regard to the heat generated between the plastic hub bush 13 and the plastic friction annulus 14, because the coefficient of thermal conduction of the material of the plastic hub bush 13 and also the coefficient of thermal conduction of the material of the plastic friction annulus 14 are both typically quite low because of the nature of these materials, this frictionally generated heat becomes trapped between the plastic hub bush 13 and the plastic friction annulus 14 and may well build up to create a high temperature, which can melt, fuse, or soften the material of the plastic hub bush 1 3 or the material of the plastic friction annulus 14, thereby causing the problems with relation to durability that have been discussed above with relation to the prior art.
However, by contrast, in the construction of the clutch disk assembly according to the shown first preferred embodiment of the present invention, because the metallic intermediate annulus 15 is included, this friction instead occurs partly between this metallic intermediate annulus 1 5 and the plastic friction annulus 14, and partly between this metallic intermedaite annulus 1 5 and the confronting face 1 3a of the plastic hub bush 1 3. Now, the amount of heat generated may very probably be more or less the same as in the above explained prior art, i.e. the actual amount of heat generated may not be particularly reduced, according to the shown construction according to the present invention; but this heat is now all generated in regions at or adjacent to the metallic intermediate annulus 15, and accordingly, because metal has a high coefficient of heat conduction, this frictionally generated heat is quickly conducted by the material of the metallic intermediate annulus 1 5 away to the outer circumference and to the inner circumference of the metallic intermediate annulus 1 5. From the inner circumference of said metallic intermediate annulus 15, the part of the heat which is conducted thereto is quickly transferred by conduction to the clutch disk hub 1 in contact therewith, said clutch disk hub 1 typically being also made of metal, and thus this heat is dissipated; while from the outer circumference of said metallic intermediate annulus 15, the part of the heat which is conducted thereto is transferred by convection and radiation to the atmosphere, and is thus also dissipated. Thereby, in the case of the shown clutch disk assembly according to the first preferred embodiment of the present invention, the danger of overheating in the portions of the construction between the shoulder portion of the plastic hub bush 1 3 and the clutch disk flange 2, which was present in the described prior art, and which in the prior art could lead to fusing, softening, and even deformation of the parts, is obviated.
Accordingly the shown clutch disk assembly according to the first preferred embodiment of the present invention is much more durable during use, and is much more reliable, than prior art type clutch disk assemblies of the sort described above, and a much more durable backing up for the pressure exerted by the friction material annul us 9 on the metallic facing friction annulus 12 coupled to the clutch disk flange 2 to provide rotational damping action when the clutch is engaged, or disengaged, is provided. This means that the shown clutch disk assembly provides good rotational damping action when the clutch is engaged or is disengaged, which acts to prevent clutch snatching, and also suppresses vibration in the drive train of the vehicle during use thereof.
Further, noises in the gear train of the vehicle are quietened down, and torque shock in the drive train of the vehicle, as during shifting of speed stage of the transmission thereof, is cushioned.
Now a second preferred embodiment of the clutch disk assembly according to the present invention will be explained, with reference to
Fig. 2. In this second preferred embodiment, the metallic intermediate annulus 1 5 is constructed to have an outer diameter which is substantially larger than the outer diameter of the plastic friction annulus 14 and which also is substantially larger than the outer diameter of the flange or shoulder portion of the plastic hub bush 13, so that the radially outward part of the metallic intermediate annulus 1 5 protrudes into the atmosphere from between said plastic hub bush 13 and said plastic friction annulus 14.This construction provides greater convective and radiative dissipation from said radially outward part of the metallic intermediate annulus 1 5 of the heat generated by friction between the plastic hub bush 13 and the metallic intermediate annulus 1 5 and of the heat generated by friction between the plastic friction annulus 14 and the metallic intermediate annulus 15, said heat being transferred to the metallic intermediate annulus 1 5 as explained above to be dissipated.
Accordingly, in this second preferred embodiment of the clutch disk assembly according to the
present invention, not only is good dissipation of the frictional heat which is transferred to the metallic intermediate annulus 1 5 available from the radially inner part of said metallic intermediate annulus 1 5 which is in contact with the clutch disk hub 1, but also good dissipation of said frictional heat which is transferred to the metallic intermediate annulus 1 5 is available from the radially outer part of said metallic intermediate annulus 1 5 which is exposed to the atmosphere; and accordingly this frictional heat is dissipated even better than in the first preferred embodiment of the clutch disk assembly according to the present invention.Therefore, this second preferred embodiment provides all the benefits of the first preferred embodiment to an even greater extent.
Although the present invention has been shown and described with reference to several preferred embodiments thereof, and in terms of the illustrative drawings, it should not be considered as limited thereby. Various possible modifications, omissions, and alterations could be conceived of by one skilled in the art to the form and the content of any particular embodiment, without departing from thescope of the present invention.
Other variations of the details of any particular embodiment could be conceived of. Therefore it is desired that the scope of the present invention, and of the protection sought to be granted by
Letters Patent, should be defined not by any of the perhaps purely fortuitous details of the shown embodiments, or of the drawings, but solely by the scope of the appended claims, which follow.
Claims (5)
1. A clutch disk assembly, comprising:
(a) a clutch disk hub with an integrally formed clutch disk flange located at an intermediate position therealong;
(b) a plastic hub bush fitted rotatably over the part of said clutch disk hub on a first side of said clutch disk flange, formed with a radially smaller portion on its side remote from said clutch disk flange and a radially larger portion on its side towards said clutch disk flange;
(c) a main disk plate formed with a central hole, said main disk plate being mounted via its central hole over said radially smaller portion of said plastic hub bush and being abutted against the side of said radially larger portion of said plastic hub bush which is remote from said clutch disk flange;;
(d) an auxiliary disk plate formed with a central hole, said auxiliary disk plate being fitted via its central hole over the part of said clutch disk hub on the side of said clutch disk flange opposite to said first side thereof:
(e) means for fixedly coupling said main disk plate and said auxiliary disk plate together both with regard to relative axial movement thereof and with regard to relative rotational movement thereof;;
(f) means for coupling said coupled combination of said main disk plate and said auxiliary disk plate to said clutch disk flange with a certain amount of rotational play being available therebetween, and for, when said rotational play is non zero in either rotational direction, exerting a spring force between said coupled combination of said main disk plate and said auxiliary disk plate and said clutch disk flange in the appropriate direction to cancel such rotational play;;
(g) means for biasing said coupled combination of said main disk plate and said auxiliary disk plate in the axial direction relative to said clutch disk hub which presses said main disk plate towards said clutch disk flange and which presses said plastic hub bush towards said clutch disk flange via said abutting contact of said main disk plate with said side of said radially larger portion of said plastic hub bush which is remote from said clutch disk flange;
(h) means for, when said coupled combination of said main disk plate and said auxiliary disk plate moves relative to the combination of said clutch disk hub and said clutch disk flange, exerting a rotational frictional damping force between said coupled combination of said main disk plate and said auxiliary disk plate and said combination of said clutch disk hub and said clutch disk flange;;
(i) a plastic friction annul us located between said side of said radially larger portion of said plastic hub bush which faces towards said clutch disk flange and the side of said clutch disk flange which faces towards said plastic hub bush; and
(j) a metallic intermediate annulus located between said side of said radially larger portion of said plastic hub bush which faces towards said clutch disk flange and the side of said plastic friction annulus which faces towards said plastic hub bush, and directly abutted against said side of said plastic friction annulus which faces towards said plastic hub bush.
2. A clutch disk assembly according to claim 1, wherein said plastic hub bush, said plastic friction annulus, and said metallic intermediate annulus are all of substantially the same outer radius.
3. A clutch disk assembly according to claim 1, wherein said metallic intermediate annulus is of substantially larger outer radius than said plastic friction annulus, and is also of substantially larger outer radius than said radially larger part of said plastic hub bush.
4. A clutch disk assembly according to claim 1, wherein the other side of said metallic intermediate annulus from the side thereof which is directly abutted against the side of said plastic friction annulus which faces towards said plastic hub bush is directly abutted against the side of said plastic hub bush which faces towards said clutch disk flange.
5. A clutch disk assembly substantially as hereinbefore described with reference to, and as illustrated in, Figure 1 or Figure 2 of the accompanying drawings.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9839881U JPS584828U (en) | 1981-07-01 | 1981-07-01 | clutch disk |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB2103758A true GB2103758A (en) | 1983-02-23 |
| GB2103758B GB2103758B (en) | 1985-08-14 |
Family
ID=14218725
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB08218928A Expired GB2103758B (en) | 1981-07-01 | 1982-06-30 | Clutch disk assembly with rotational damping construction including heat dissipating metal plate |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPS584828U (en) |
| AU (1) | AU553506B2 (en) |
| GB (1) | GB2103758B (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2554886A1 (en) * | 1983-11-11 | 1985-05-17 | Fichtel & Sachs Ag | CLUTCH PLATE FOR A FRICTION CLUTCH OF A MOTOR VEHICLE |
| US4651860A (en) * | 1984-06-19 | 1987-03-24 | Kabushiki Kaisha Daikin Seisakusho | Clutch disk supported by a resin bushing |
| DE3544500A1 (en) * | 1985-12-17 | 1987-06-19 | Fichtel & Sachs Ag | CLUTCH DISC WITH PLASTIC MOLDED PLASTIC BEARING ELEMENTS |
| FR2614379A1 (en) * | 1987-04-22 | 1988-10-28 | Valeo | TORSION DAMPING DEVICE |
| US4848552A (en) * | 1985-03-06 | 1989-07-18 | Kabushiki Kaisha Daikin Seisakucho | Damper disc |
| FR2669390A1 (en) * | 1990-11-16 | 1992-05-22 | Valeo | TORSION DAMPER DEVICE, IN PARTICULAR FOR CLUTCH FRICTION OF MOTOR VEHICLES. |
| DE3546918C2 (en) * | 1985-10-19 | 1996-11-07 | Fichtel & Sachs Ag | Plate clutch for vehicle transmission |
| EP1457708A2 (en) * | 2003-03-14 | 2004-09-15 | Aisin Seiki Kabushiki Kaisha | A torsional damper apparatus |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2535942Y2 (en) * | 1990-10-04 | 1997-05-14 | 富山科学工業株式会社 | Inner stopper for liquid container |
| DE4444660C1 (en) * | 1994-12-15 | 1996-05-30 | Fichtel & Sachs Ag | Clutch disc with balancing rivets |
-
1981
- 1981-07-01 JP JP9839881U patent/JPS584828U/en active Granted
-
1982
- 1982-06-29 AU AU85449/82A patent/AU553506B2/en not_active Ceased
- 1982-06-30 GB GB08218928A patent/GB2103758B/en not_active Expired
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2554886A1 (en) * | 1983-11-11 | 1985-05-17 | Fichtel & Sachs Ag | CLUTCH PLATE FOR A FRICTION CLUTCH OF A MOTOR VEHICLE |
| DE3340896A1 (en) * | 1983-11-11 | 1985-05-23 | Fichtel & Sachs Ag, 8720 Schweinfurt | Torsional vibration damper with play-free storage and defined friction |
| US4635780A (en) * | 1983-11-11 | 1987-01-13 | Fichtel & Sachs Ag | Clutch disc for a motor vehicle friction clutch |
| US4651860A (en) * | 1984-06-19 | 1987-03-24 | Kabushiki Kaisha Daikin Seisakusho | Clutch disk supported by a resin bushing |
| US4848552A (en) * | 1985-03-06 | 1989-07-18 | Kabushiki Kaisha Daikin Seisakucho | Damper disc |
| DE3546918C2 (en) * | 1985-10-19 | 1996-11-07 | Fichtel & Sachs Ag | Plate clutch for vehicle transmission |
| DE3544500A1 (en) * | 1985-12-17 | 1987-06-19 | Fichtel & Sachs Ag | CLUTCH DISC WITH PLASTIC MOLDED PLASTIC BEARING ELEMENTS |
| FR2614379A1 (en) * | 1987-04-22 | 1988-10-28 | Valeo | TORSION DAMPING DEVICE |
| FR2669390A1 (en) * | 1990-11-16 | 1992-05-22 | Valeo | TORSION DAMPER DEVICE, IN PARTICULAR FOR CLUTCH FRICTION OF MOTOR VEHICLES. |
| EP1457708A2 (en) * | 2003-03-14 | 2004-09-15 | Aisin Seiki Kabushiki Kaisha | A torsional damper apparatus |
| EP1457708A3 (en) * | 2003-03-14 | 2005-01-05 | Aisin Seiki Kabushiki Kaisha | A torsional damper apparatus |
Also Published As
| Publication number | Publication date |
|---|---|
| AU553506B2 (en) | 1986-07-17 |
| JPS6332986Y2 (en) | 1988-09-02 |
| AU8544982A (en) | 1983-01-06 |
| JPS584828U (en) | 1983-01-12 |
| GB2103758B (en) | 1985-08-14 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PCNP | Patent ceased through non-payment of renewal fee |
Effective date: 19970630 |