GB2124734A - Clutch disc for a friction clutch - Google Patents
Clutch disc for a friction clutch Download PDFInfo
- Publication number
- GB2124734A GB2124734A GB08318433A GB8318433A GB2124734A GB 2124734 A GB2124734 A GB 2124734A GB 08318433 A GB08318433 A GB 08318433A GB 8318433 A GB8318433 A GB 8318433A GB 2124734 A GB2124734 A GB 2124734A
- Authority
- GB
- United Kingdom
- Prior art keywords
- hub flange
- plate
- driven plate
- friction
- side plates
- 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
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—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 using springs as elastic members, e.g. metallic springs
- F16F15/123—Wound springs
- F16F15/1238—Wound springs with pre-damper, i.e. additional set of springs between flange of main damper and hub
Landscapes
- 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 hub (1) has a radial flange (5) on which driven plate (7) with clutch friction linings (13) is mounted for rotation through a limited angle. Side plates (15, 17) are connected fast in rotation with one another and are rotatable through a limited angle in relation to the flange (5) and plate (7). Main torsion damping springs (33) act between the driven plate (7) and the side plates (15, 17), and second torsion damping springs (31) act between the side plates and flange (5). A pressure plate (35, 37), which is initially stressed by at least one spring (39, 41, 47, 49) supported on the side plates (15, 17) is fast in rotation but displaceable axially at least between one of the two side plates (15, 17) and the flange (5) or the driven plate (7). The pressure plate (35, 37) is in frictional contact both with the flange (5) and with the driven plate (7) through friction plates (53, 55). Instead of through a separate pressure plate, one of the side plates can also be in direct frictional contact with the axially adjacent friction plate. The friction plates (53, 55) are connected preferably integrally with bearing rings (61, 63) which mount the driven plate (7) on the hub flange (5). <IMAGE>
Description
SPECIFICATION
Clutch disc for a friction clutch
The invention relates to a clutch disc with torsional vibration damper for a friction clutch, especially of a motor vehicle.
From U.S. Patent No. 3,128,640 a clutch disc for a motor vehicle friction clutch is known the hub of which carries a radially protruding hub flange and, mounted on the hub flange rotatably through a limited angle of rotation, a driven plate provided with clutch friction linings. On both sides of the hub flange and the driven plate there are arranged side plates which are connected with one another by rivets. The rivets pass through slots of the driven plate so that the side plates are rotatable through a limited angle of rotation in relation to the hub flange and the driven plate. Helical springs are seated in windows of the hub flange and of the side plates and are stressed on relative rotation of the hub flange and the side plates. The helical springs form a torsion pre-damper which damps the vibrations occurring in idling.Further helical springs are arranged in windows of the driven plate and of the side plates. These helical springs are stressed in the relative rotation between the driven plate and the side plates and form a torsion main damper, which damps the vibrations occurring under load at higher rotation rates. The side plates lie with their radially inwardly situated regions against the hub flange and form a first friction damper. A further friction damper is formed by additional annular plates which are secured to the driven plate and abut with their radially inner regions in frictional manner against the hub flange. In the known clutch disc the initial stress force which determines the friction torque is applied by the inherent elasticity of the side plates and of the annular plates. The friction torque cannot be predetermined exactly and is difficult to adjust in defined manner.
it is the problem of the invention to indicate a clutch disc with two friction-damped spring damper devices effective in series, in which the initial stress force of the friction damping devices is generated by common springs.
Within the scope of the invention this is achieved in that in a clutch disc of the above-explained known type a pressure plate guided fast in rotation but axially movably on the side plates is provided at least between one of the two side plates and the hub flange or the driven plate, which pressure plate is initially stressed axially towards the hub flange and the driven plate by a spring supported on the side plate. The pressure plate is here in frictional contact both with the hub flange and with the driven plate.
By suitable dimensioning of the surfaces which are in frictional contact and by suitable selection of the coefficient of friction of the friction plates arranged between the pressure plate and the hub flange or the driven plate it is possible in a constructionally simple manner to dimension the friction torques exerted upon the hub flange and the driven plate. To generate the axial initial stress forces both for the friction torque acting upon the hub flange and for the friction torque acting upon the driven plate, common springs are provided.
In preferred forms of embodiment annular friction plates are provided axially on both sides of the hub flange and also of the driven plate. On each side there can be present a single friction plate utilised in common both by the hub flange and by the driven plate; however alternatively separate friction plates, especially with mutually different coefficients of friction, can be associated with the hub flange and the driven plate.
The annular driven plate is mounted preferably through at least one bearing ring with good sliding properties on the external circumference of the hub flange. Expediently each bearing ring is connected fixedly, especially integrally, with one of the friction plates.
The two side plates can be secured to one another by distance-retaining rivets, preferably in the region of their external edge and in the region of the internal edge. The distance rivets here pass through slots in the driven plate and the hub flange and at the same time limit the angle of rotation of the side plates in relation to the hub flange and the driven plate. The springs which initially stress the pressure plate axially against the hub flange and the driven plate can be leaf springs which are secured at one end by means of the distance rivets to the side plates. The leaf springs are fitted on the outside of the side plates and extend with their ends remote from the rivets through openings in the side plates.
The leaf springs can also be the tongues of an annular diaphragm spring or the like fitted on the outside of the side plate. A dished spring or likewise a diaphragm spring can also be arranged between the side plate and the adjacent pressure plate, while noses formed on the side plate centre the dished spring and fix it radially.
In clutch discs according to the invention driven plate can be rotated in relation to the hub under frictional damping and spring damping over especially large angles of rotation. The clutch disc therefore can be used not only in conventional separator clutches between engine and transmission of a motor vehicle, but also for bridge-over clutches in torque converters. The relatively great rotation distance can be divided upon without problem so that with relatively slight pre-damping a comparatively great rotation distance is travelled while after commencement of the main damping the damping force can be increased considerably. The rotation distances available for the pre-damping and main damping are determined by the rotation angle limitations of the driven plate in relation to the side plates and of the side plates in relation to the hub flange.
Examples of embodiment of the invention are to be explained in greater detail below by reference to drawings, wherein:
Figure 1 shows a section through a clutch disc of a motor vehicle friction clutch with leaf springs arranged on both axial sides to generate the initial stress force of a two-stage friction damping device;
Figure 2 shows a section through another form of embodiment of the clutch disc with leaf springs arranged on one axial side;
Figure 3 shows a section through a third form of embodiment of a clutch disc with a dished spring generating the initial stress force of a two-stage friction damping device, and
Figures4to 6show sections through a detail of further clutch discs which is usable alternatively in the clutch discs according to Figures 1 to 3.
Figure 1 shows a hub 1 which is couplable fast in rotation with a gear input shaft (not shown further) which is rotatable about a rotation axis 3. The hub 1 carries a radially protruding hub flange 5 on the external circumference of which an annular driven plate 7 is rotatably mounted in a manner explained in greater detail hereinafter. An annular lining carrier plate 11, in turn carrying clutch friction linings 13 on both axial sides, is secured with rivets 9 on the driven plate 7. Side plates 15, 17 are mounted rotatably on the hub 1 by means of bearing rings 19, 21 on both axial sides of the hub flange 5 and the driven plate 7.In the regions of both the internal circumference and the external circumference of the side plates 15, 17 distance rivets 23 and 25 respectively are provided in distribution in the circumferential direction, connecting the side plates 15, 17 firmly with one another. The distance rivets 23 pass through elongated holes or slots 27 of the hub flange 5 which extend in the circumferential direction. The distance rivets 25 in corresponding manner pass through slots 29 in the driven plate 7. The distance rivets 23 and the slots 27 limit the angle of rotation of the side plates 15, 17 in relation to the hub flange 5.
The distance rivets 25 and the slots 29 limit the angle of rotation of the driven plate 7 in relation to the side plates 15, 17.
Compression springs indicated at 31 are seated in windows (not shown further) of the hub flange 5 on the one part and of the side plates 15, 17 on the other, which springs on relative rotation of the side plates 15,17 and of the hub flange 5 are stressed and have a damping effect. The compression springs 31 form a pre-damperwhich is effective in the idling range. In an analogous manner compression springs indicated at 33 are seated in windows (not shown further) of the driven plate 7 and of the side plates 15, 17 and are stressed on relative rotation of the driven plate 7 and the side plates 15,17. The compression springs 33 damp torsional vibrations in operation under load and form a main damper the effect of which commences after bridging over of the pre-damper and causes the damping force to increase.
On both axial sides of the hub flange 5 and of the driven plate 7 there are arranged pressure plates 35 and 37 which annularly surround the hub 1. The pressure plates 35, 37 are guided fast in rotation but axially displaceably on the distance rivets 25 and are resiliently initially stressed by leaf springs 39, 41 axially towards the hub flange 5 and the driven plate 7. The leaf springs 39,41 are secured at one end by means of the distance rivets 25 on the side of the side plates 15,17 axially remote from the pressure plates 35,37 and extend substantially radially and engage with their free ends, abutting on the pressure plate 35 and 37, through openings 43, 45 of the adjacent side plate 15,17 in each case.Further leaf springs 47, 49 are entered in chain lines in Figure 1 and extend in conformity with the leaf springs 39, 41 but are secured to the radially inwardly situated distance rivets 23. The leaf springs 47,49 can be provided in place of the leaf springs 39,41 or additionally.
Friction plates 53, 55 which annularly and coaxially surround the hub 1 are provided on both sides of the hub flange 5 and guided on radial shoulders 51 of the hub flange 5. The friction plates 53, 55 are in frictional contact over their entire radial width with the adjacent pressure plates 35 and 37 and are on the one hand in frictional contact over a radial distance 57 with the hub flange 5 and also in frictional contact over a distance 59 with the driven plate 7. The distances 57, 59 and thus the areas transmitting the friction moment arse dimensioned in accordance with the friction moments desired for the pre-damping and main damping.
Annular protuberances 61 and 63 respectively, concentric with the rotation axis 3, are formed integrally on the friction plates 53, 55, extend radially between the hub flange 5 and the driven plate 7 and are utilised as bearing rings for the mounting ofthe driven plate 7 on the hub flange 5.
Figure 2 shows another form of embodiment of a clutch disc for a motor vehicle friction clutch which differs from the clutch disc according to Figure 1 essentially only in that one of the two pressure plates including the associated leaf springs is omitted and one of the two side plates is in direct frictional contact with the adjacent friction plate. The elements 1 to 15, to 33,39,43,47 and 53 to 63 of the clutch disc as illustrated in Figure 2 correspond to the elements of the clutch disc according to Figure 1 designated by the same numbers. Therefore for explanation reference will be made to the above description of these elements.
The side plate 17a corresponding to the side plate 17, of the clutch disc according to Figure 2 is in direction frictional contact with the friction plate 55 and is initially stressed by the leaf springs 39 and 47 supported on the pressure plate 35a axially towards the hub flange 5 and the driven plate 7. The pressure plate 35a, in contrast to the pressure plate 35 of the clutch disc according to Figure 1, is guided axially displaceably but fast in rotation on the radially inwardly placed distance rivets 23. As Figure 2 shows, the annular shoulders 51 which centre and radially fix the friction plates 53, 55 can be omitted provided that bearing protuberances 61 and 63 are provided on the friction plates 53, 55.
Figure 3 shows a clutch disc which corresponds substantially to the clutch disc according to Figure 2, except that in place of the leaf springs 39 and 47 a dished spring or diaphragm spring 65 is provided which initially stresses the pressure plate 35a axially against the hub flange 5 and the driven plate 7. The diaphragm spring 65 annularly encloses the hub 1 and is arranged axially between a side plate 15a and the pressure plate 35a. Several noses 67 protruding axially to the pressure plate 35a are bent out of the side plate 15a and-centre and radially guide the diaphragm spring 65. Otherwise the elements 1 to 13, 15a, 17a, 19 to 33, 35a and 53 to 63 correspond to the elements in Figure 2 designated by the same numbers. For the explanation of these elements reference is made to the description of Figures 1 and 2.
Figures 4 to 6 show variants for the mounting of the driven plate on the hub flange and the development of the friction plates which can be used in the clutch discs according to Figures 1 to 3.
Figure 4 shows the radially outer region of a hub flange 5a on which a driven plate 7a is mounted rotatably be means of a bearing ring 69 of slidable material surrounding the hub flange 5a. Axially on both sides of the hub flange 5a and of the driven plate 7a there are arranged friction plates 71 and 73 which annularly surround the rotation axis of the clutch disc. In contrast to the friction plates 53, 55 as represented in Figures 1 to 3, the bearing ring 69 is not connected with the friction plates 71,73. Radial shoulders 51a of the hub flange 5a centre and fix the friction plates 72, 73.
In the form of embodiment according to Figure 5 a driven plate 7b is again mounted rotatably through a bearing ring 69b on a hub flange Sb. In contrast to the form of embodiment according to Figure 4 the friction plates do not extend in common both over the hub flange Sb and the driven plate 7b. Axially on both sides of the hub flange 5b friction plates 75 and 77 are arranged concentrically with the axis of rotation of the clutch disc. The friction plates 75,77 are centred and radially fixed by radial shoulders 79 of the hub flange 5b. Axially on both sides of the driven plate 7b there are provided friction plates 81, 83 which annularly surround the rotation axis of the clutch disc and are centred and radially fixed by the radial shoulders 85 of the driven plate 7b. The friction plates 81,83 consist of a material of higher coefficient of friction than the friction plates 75, 77.
The bearing ring 69b consists of a material with low friction.
Figure 6 shows a form of embodiment with a driven plate 7c mounted on a hub flange 5c, which differs from the form of embodiment according to
Figure 5 essentially only in that bearing rings 87, 89 arranged radially between the hub flange Sc and the driven plate 7c are connected integrally fast with the friction plates 75c and 77c arranged axially on both sides of the hub flange 5c. The friction plates 75c and 77c correspond to the friction plates 75, 77 in Figure 5. The driven plate 7c carries friction plates 81 c and 83c separates therefrom, which correspond to the friction plates 81,83 in Figure 5.
Claims (12)
1. Clutch disc for a friction clutch having a hub (1) defining a rotation axis (3) which carries fast in rotation a radially protruding hub flange (5), having an annular driven plate (7) coaxially enclosing the hub flange (5) and rotatable in relation to the hub flange (5) through a limited angle of rotation about the rotation axis (3), to which driven plate clutch friction linings (13) are secured, having two side plates (15, 17) arranged on axially opposite sides laterally of the hub flange (5) and the driven plate (7), connected fast in rotation with one another and rotatable through a limited angle of rotation in relation to the hub flange (5) and to the driven plate (7) about the rotation axis (3), having first damper springs (33) stressable in the relative rotation of the driven plate (7) and the side plates (15, 17), having second damper springs (31) stressable in the relative rotation of the side plates (15, 17) and of the hub flange (5), and having an axially resiliently initially stressed friction damper device (39, 41,47,49 53, 55; 65; 71,73; 75, 77, 81,83) in the relative rotations of the driven plate (7), the side plates (15, 17) and the hub disc (5), characterised in that the friction damper device comprises axially at least between one of the two side plates (15, 17) and the hub flange (5) or the driven plate (7) a pressure plate (35, 37) guided fast in rotation but axially movably on the side plates (15, 17), in that at least one spring (39,41,47,49; 65) supported on the side plates (15, 17) initially stresses the pressure plate (35,37) axially to the hub flange (5) or the driven plate (7) and in that the pressure plate (35, 37) is in frictional contact both with the hub flange (5) and with the driven plate (7).
2. Clutch disc according to Claim 1, characterised in that on each of the two axial sides of the hub flange (5) and the driven plate (7) a pressure plate (35,37) is arranged axially between the side plate (15, 17) and the hub flange (5) or the driven plate (7), which pressure plate is in frictional contact both with the hub flange (5) and with the driven plate (7), and in that axially on both sides of the hub flange (5) and the driven plate (7) springs (39, 41, 47,49) are supported on the side plates (15, 17) and initially stress the pressure plates (35,37) axially towards one another.
3. Clutch disc according to Claim 1, characterised in that a pressure plate (35a) is provided only on one side of the hub flange (5) and the driven plate (7) and in that the side plate (17a) arranged on the side of the hub flange (5) and the driven plate (7) axially remote from the pressure plate (35a) is in frictional contact both with the hub flange (5) and with the driven plate (7) axially remote from the pressure plate (35a) is in frictional contact both with the hub flange (5) and with the driven plate (7).
4. Clutch disc according to one of Claims 1 to 3, characterised in that axially on both sides of the hub flange (5) and the driven plate (7) there are arranged friction plates (53, 55; 71,73; 75, 77, 81, 83), the area and/or coefficient of friction of which are so dimensioned that the frictional torque transmitted in the relative rotation of the side plates (15, 17) and of the hub flange (5) and the frictional torque transmitted in the relative rotation of the driven plate (7) and of the side plates (15, 17) are of different magnitudes.
5. Clutch disc according to Claim 4, characterised in that on each of the two sides of the hub flange (5) and the driven plate (7) there is arranged a single annular friction plate (53,55; 71,73) which overlaps radially both the hub flange (5) and the driven plate (7).
6. Clutch disc according to Claim 5, characterised in that the area of the friction plates (53, 55; 71,73) overlapping the hub flange (5) is smaller than the area overlapping the driven plate (7).
7. Clutch disc according to Claim 4, characterised in that one each of the two sides of the hub flange (5) an annular first friction plate (75, 77) is arranged and on each of the two sides of the driven plate (7) a second annular friction plate (81,83) is arranged.
8. Clutch disc according to Claim 7, characterised in that the second friction plates (81,83) consist of a material having a greater coefficient of friction than the first friction plates (75, 77).
9. Clutch disc according to one of Claims 4 to 8, characterised in that at least one bearing ring (61,63; 87,89) rotatably carrying the driven plate (7) on the hub flange (5) is arranged radially between the hub flange (5) and the driven plate (7) and in that each bearing ring (61, 63; 87, 89) is firmly connected with one of the friction plates (53,55; 75,77) arranged lateraily of the hub flange (5) and of the driven plate (7).
10. Clutch disc according to one of Claims 1 to 9, characterised in that the side plates (15, 17) are connected with one another by rivets (23, 25) and in that a spring device comprising several substantially radially extending leaf springs (39,41, 47, 49) is secured by means of the rivets (23, 25) on the side of at least one of the two side plates (15,17) axially remote from the hub flange (5) or the driven plate (7), and in that in the side plate (15, 17) adjacent to the leaf springs (39,41,47,49) there are provided openings (43,45) through which the free ends of the leaf springs (39,41,47, 49) extend and abut on the pressure plate (35, 37).
11. Clutch disc according to one of Claims 1 to 9, characterised in that an annular dished spring or diaphragm spring (65) is arranged axially between at least one of the two side plates (15a) and the adjacent pressure plate (35a) and in that noses (67) are formed on the side plate (15a) and radially fix the dished spring or diaphragm spring (65).
12. A clutch disc for a friction clutch substantially as herein described with reference to Figures 1 to 6 of the accompanying drawings.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19823227991 DE3227991A1 (en) | 1982-07-27 | 1982-07-27 | CLUTCH DISC WITH TORSION DAMPER AND COMMON SPRING FOR FRONT AND MAIN DAMPING |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| GB8318433D0 GB8318433D0 (en) | 1983-08-10 |
| GB2124734A true GB2124734A (en) | 1984-02-22 |
| GB2124734B GB2124734B (en) | 1985-10-23 |
Family
ID=6169433
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB08318433A Expired GB2124734B (en) | 1982-07-27 | 1983-07-07 | Clutch disc for a friction clutch |
Country Status (3)
| Country | Link |
|---|---|
| DE (1) | DE3227991A1 (en) |
| FR (1) | FR2532026A1 (en) |
| GB (1) | GB2124734B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4941860A (en) * | 1988-01-13 | 1990-07-17 | Valeo | Coaxial torsion damper, particularly for automotive vehicles |
| US6224487B1 (en) | 1997-04-02 | 2001-05-01 | Borgwarner Inc. | Two stage torsional vibration damper |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2565650B1 (en) * | 1984-06-12 | 1990-04-27 | Luk Lamellen & Kupplungsbau | DEVICE FOR COMPENSATING FOR ROTATION |
| JPS616028U (en) * | 1984-06-19 | 1986-01-14 | 株式会社 大金製作所 | clutch disc |
| DE3537324C2 (en) * | 1985-10-19 | 1995-09-14 | Fichtel & Sachs Ag | Torsional vibration damper |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2109085A (en) * | 1981-11-14 | 1983-05-25 | Fichtel & Sachs Ag | Clutch disc with torsional vibration damper |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1840718U (en) * | 1961-08-19 | 1961-11-02 | Fichtel & Sachs Ag | CLUTCH DISC WITH VIBRATION DAMPER FOR FRICTION CLUTCHES, IN PARTICULAR FOR MOTOR VEHICLES. |
| US3128640A (en) * | 1962-02-09 | 1964-04-14 | Borg Warner | Vibration dampeners |
| FR1349574A (en) * | 1962-02-09 | 1964-01-17 | Borg Warner | Vibration damper, especially for clutch |
| DE1530543A1 (en) * | 1965-02-26 | 1970-02-26 | Daimler Benz Ag | In particular, torsionally elastic element arranged between the friction disk and its hub part of motor vehicle clutches |
| FR2097289A5 (en) * | 1970-07-01 | 1972-03-03 | Ferodo Sa | |
| IT980940B (en) * | 1972-02-11 | 1974-10-10 | Fichtel & Sachs Ag | CLUTCH DISC ESPECIALLY FOR VEHICLES WITH TORSIONAL SWING DAMPER FOR RUNNING AT IDLE AND UNDER LOAD |
| FR2398927A1 (en) * | 1977-07-27 | 1979-02-23 | Stichler Bernd | Main clutch assembly for motor vehicle - has different stiffness damping springs and multiple slotted pads on pressure plate |
| DE8215539U1 (en) * | 1982-05-28 | 1982-09-30 | Fichtel & Sachs Ag, 8720 Schweinfurt | Torsional vibration damper with backlash-free friction device |
-
1982
- 1982-07-27 DE DE19823227991 patent/DE3227991A1/en active Granted
-
1983
- 1983-07-07 GB GB08318433A patent/GB2124734B/en not_active Expired
- 1983-07-27 FR FR8312747A patent/FR2532026A1/en not_active Withdrawn
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2109085A (en) * | 1981-11-14 | 1983-05-25 | Fichtel & Sachs Ag | Clutch disc with torsional vibration damper |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4941860A (en) * | 1988-01-13 | 1990-07-17 | Valeo | Coaxial torsion damper, particularly for automotive vehicles |
| US6224487B1 (en) | 1997-04-02 | 2001-05-01 | Borgwarner Inc. | Two stage torsional vibration damper |
Also Published As
| Publication number | Publication date |
|---|---|
| DE3227991C2 (en) | 1990-09-13 |
| GB2124734B (en) | 1985-10-23 |
| FR2532026A1 (en) | 1984-02-24 |
| GB8318433D0 (en) | 1983-08-10 |
| DE3227991A1 (en) | 1984-02-02 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PCNP | Patent ceased through non-payment of renewal fee |