GB2235749A - Friction clutch driven plate - Google Patents
Friction clutch driven plate Download PDFInfo
- Publication number
- GB2235749A GB2235749A GB8919878A GB8919878A GB2235749A GB 2235749 A GB2235749 A GB 2235749A GB 8919878 A GB8919878 A GB 8919878A GB 8919878 A GB8919878 A GB 8919878A GB 2235749 A GB2235749 A GB 2235749A
- Authority
- GB
- United Kingdom
- Prior art keywords
- hub
- plate
- annular
- ribs
- friction clutch
- 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
- F16F15/1215—Leaf springs, e.g. radially extending
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/80—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive in which a fluid is used
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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
- F16F15/121—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
-
- 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
- F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
A friction clutch driven plate comprising a hub (11) a friction facing carrier (14) mounted on the hub, and a damper (50) operably located between the facing carrier and hub to resist rotational movement therebetween. The damper (50) comprises two relatively rotatable parts (40, 41) arranged coaxially of the hub, the first part (40) being fixed with the hub, and the second part (41) being fixed with facing carrier, and a viscous fluid located in a chamber formed between said two parts to act as a viscous damper to oppose relative rotational movement between said two parts. The two parts (40, 41) comprise annular plates each having two radially spaced axially extending annular ribs thereon, the ribs on two plates extending in opposite directions to provide pairs of annular surfaces having seals therebetween to define said chamber. <IMAGE>
Description
FRICTION CLUTCH DRIVEN PLATES
This invention relates to friction clutch driven plates, and in particular, but not exclusively, to friction clutch driven plates for use on vehicles.
In a typical motor vehicle the engine is connected to the vehicle gearbox via a friction clutch which includes a fly wheel and pressure plate connected to the engine, and between which is sandwiched a driven plate which is connected to the gearbox.
A friction clutch driven plate typically comprises a hub which is splined onto the gearbox input shaft, a co-axial friction facing carrier plate mounted on the hub and capable of limited angular rotation about the hub, and springs housed in aligned apertures in a flange connected to the hub and the carrier plate, to act between the hub and carrier plate to restrain said angular rotation. The facing carrier plate is connected to the vehicle flywheel through the friction facings.
The movement of the facing carrier around the hub is usually dampened by a friction damper unit so as to introduce more hysterises into the system. Even so the driven plate may ive rise to so called "drive noises".
In some vehicles when the engine is idling and there is no torque load passing through the clutch driven plate the irregular impulses from the vehicle engine can be transmitted to the gearbox and cause gearbox idle chatter.
Solutions to overcome this problem have involved the use of multi-stage spring damping in which the movement between the friction facing carrier plate and the hub flange is dampened by main or second stage damping springs and the hub flange is free to rotate through a limited angular movement relative to the hub drive and is restrained in this movement by a very low rate first stage torsional damping spring or springs. The hub flange can oscillate around the hub when the vehicle is idling with only the first stage damping springs operating to suppress any transmission of vibrations to the gearbox.
The present invention provides a new form of friction clutch driven plate damper which can be utilised to reduce both drive noise and idling noises.
According to the present invention there is provided a friction clutch driven plate comprising a hub and a friction facing carrier mounted coaxially on the hub for limited rotation. movement about the hub, and a damper operably located between the facing carrier and hub to resist said rotational movement, characterised in that said damper comprises two relatively rotatable parts arranged coaxially of the hub, one of said parts being rotatable with the hub, and the other of said parts being rotatable with the facing carrier, and a viscous fluid is located in a chamber formed between said two parts so as to act therebetween as a viscous damper to oppose relative rotational movement between said two parts.
Preferably, one of said rotatable parts comprises an annular plate housing two radially spaced axially extending annular ribs thereon, and the other of said two rotatable parts is a second annular plate also having two radially spaced and axially but oppositely extending ribs thereon, the oppositely extending ribs on the two plates providing pairs of annular sealing surfaces to define said chamber in which the viscous fluid is located.
Conveniently the driven plate also includes an annular hub flange projecting radially outwardly from the hub and one of said rotatable parts is rotationally fast with the facing carrier, and the other of the rotatable parts is rotationally fast with the hub so as to provide viscous damping over the whole phase of rotational movement of the facing carrier around the hub.
Alternatively the driven plate may include an annular hub flange which is mounted coaxially on the hub and is capable of limited angular rotation relative to the hub, and one of said rotatable parts is fast with the hub flange and the other of said rotatable parts is fast with the hub ,so as to provide viscous damping only during the period of rotation of the hub flange relative to the hub.
The invention will now be descibed with reference to the accompanying drawings in which
FIG 1 is an elevation of a clutch driven plate according to the invention,
FIG 2 is a section on the line II-II of Fig. 1,
FIG 3 is an enlargement of the center of the driven plate as is shown in Fig. 2,
FIG 4 is a front elevation with the viscous damper removed showing the return springs located between the hub and hub flange,
FIG 5 is an enlargement of the center of a modified driven plate,
FIG 6 is an enlargement of a detail of the viscous damper showing a modification to the viscous damper.
With reference to Figs. 1 to 4, there is illustrated a friction clutch driven plate for a motor vehicle and which comprises a hub 11 having internal splines 13 for connection with a gearbox input shaft and an annular array of circumferentially spaced teeth 20 (see Fig. 4) extending radially outwards on the outer surface of the hub 11.
A coaxial annular flange 12 having spaced teeth 30 in its inner peripheral margin is mounted on the hub 11 concentrically with the teeth 20 so that the teeth 20 loosely engage teeth 30 allowing the flange 12 limited angular movement about the hub 11. A coaxial friction facing carrier 14 is also mounted on the hub 11 and is capable of limited angular movement relative to both the flange 12 and the hub 11. A set of main torsion damping springs 15 are housed in aligned apertures 16 and 17 in the hub flange 12 and facing carrier 14 respectively, and act to restrain the angular movement therebetween.
Although the number of springs illustrated is a preferred six springs, there is no reason why other numbers of springs cannot be used for example between four springs and eight springs.
The annular facing carrier 14 comprises an annular carrier plate 18 located to one axial side of the flange 12, and an annular retainer plate 19 disposed on the other axial side of the flange 12. The two annular plates 18 and 19 are secured together by three stop pins 21 which pass through co-operating apertures 32 in the outer peripheral margin of the flange 12. The stop pins 21 limit the rotational movement of the facing carrier 14 about the hub 11 and flange 12 by abutment against the radial ends of the apertures 32.
A plurality of segments 23 are arranged in a circular array and are attached to the outer peripheral margin of the carrier plate 18 by any suitable means such as rivets, and a pair of opposed annular friction facings 24 are secured one on each side of the segments 23 by suitable means such as rivets. The segments 23 typically are of spring steel and are shaped to provide resilient axial cushioning between the two friction facings.
Now as best seen in Fig. 3, a friction damping washer 26 is located axially between the teeth 20 on the hub, and an annular plate 40 forming part of a viscous damper 50 to be described later. A first spring washer 27, located between the carrier plate 18 and the hub flange 12 biases the hub flange 12 against a spacer ring 44, to be described later.
A second spring washer 29 is located axially outwardly of the carrier plate 18 and acts against an annular abutment 31 to bias the carrier plate 18 towards the teeth 20 on the hub so as to help take out tolerances and to provide some friction damping.
The main damping springs 15 are housed in the aligned apertures (sometimes referred to as spring windows) 16, in the hub flange 12, and apertures 17 in the carrier plate 18 and retainer plate 19. The spring windows 16 and 17 have circumferential ends that are contactable with the ends of the springs 15 during the rotational movement of the carrier 14 around the hub 11 to compress the springs 15. The main damping springs may all act simultaneously or can be brought into operation after different angular phases of rotation, as is well known in the trade.
The teeth 20 on the hub 11 are engaged with the teeth 30 on the inner peripheral margin of flange 12 so that the flange 12 is capable of limited angular rotation around the hub 11. The angular rotation of the flange 12 around the hub 11 being limited in both directions of rotation by abutment of teeth 20 with the teeth 30.
The rotational movement between the hub flange 12 and the hub 11 is resisted by the viscous damper 50.
The viscous damper 50 comprises two relatively rotatable parts, a first annular plate 40 and a second annular plate 41 with a viscous fluid acting therebetween . The first annular plate 40 is made rotationally fast with the hub flange 12 by axial projections 42 that extend from its back face so as to engage with the teeth 30 on the hub flange. The second annular plate 41 is made rotationally fast with the hub 11 by tags 43 that engage with teeth 62 on the outer surface of the hub 11. An annular spacer ring 44 is located radially outwardly of the viscous damper 50 and extends between the hub flange 12 and the retainer plate 19. The spacer 44 is made rotationally fast with the flange 12 by engaging in radially inward extensions of the hub flange spring window 16.
The first annular plate 40 forms a male plate and has a pair of radially spaced annular ribs 45 or 46 thereon extending axially away from the hub flange 12. The second annular plate 41 forms a female plate and also has a pair or radially spaced annular ribs 47 and 48 thereon that extend axially towards the hub flange 12 so that the ribs 48 and 47 form a female pair which envelope the ribs 45 and 46 forming a male pair so that the ribs 46 and 47 and the ribs 45 and 48 define pairs of sealing surfaces each having an annular seal 49, located therebetween, to define a chamber 51 in which a viscous fluid is located.
As can be seen in Fig. 3 the ribs 47 and 48 are located respectively radially outwardly and radially inwardly of the ribs 46 and 45 on the male plate 40.
The chamber 51 formed between the two ribs 45 and 46 on the male plate 40 is divided by radial ribs or vanes into a plurality of circumferentially spaced arcuate cavities which are linked by passageways so that each cavity is connected to its neighbouring chambers by at least one passageway to allow the flow through of viscous fluid.
The female plate 41 has an annular array of paddles 52 thereon which are each aligned with and project into a respective cavity so that relative rotation between the plates 40 and 41 moves each paddle 52 in its cavity to cause the viscous fluid to flow either around the paddle 52, and/or through the passageways to generate the viscous damping.
As best seen in Fig.4, the teeth 30 on the hub flange 12 have notches 30A therebetween which are radially elongated to recieve leaf springs 60 fitted to teeth 20A on the hub 11 for centering the flange 12 to "at rest" position relative to the hub 11. There are three equiangularly spaced -notches 30A and their respective leaf springs.
The operation of the driven plate will now be explained also with reference to Figs. 1 to 4. With the hub 11 held stationary and a drive load applied to the friction facings 24, the facing carrier 14 is moved anti-clockwise as shown by arrow X in Fig. 1. Since carrier 14 and flange 12 are held rotationaly fast by the main torsion damping springs 15, the flange 12 will initially move with the carrier 14 relative to the hub 11 to take up the clearance between the teeth 20 and 30. The male plate 40 is held rotationally fast to the hub flange 12 by the projections 30, and the female plate 41 is held fast to the hub 11 by the tabs 43.Therefore the initial resistance to rotational movement of the facing carrier 14 is due ot the viscous damping generated by the relative movement of the two plates 40 and 41 and by the leaf springs 60 together, with some friction damping generated by the washer 26 and the interface between the hub 11 and carrier plate 18.
This continues until the lost-motion clearance between the teeth 30 on the hub flange 12, and the teeth 20 on the hub 11, is taken up (see Fig. 1A). This effectively ends the operation of the viscous damper.
When the lost motion movement between the teeth 20 the teeth 30 have been taken up, further anti-clockwise movement causes the compression of the main torsion springs 15 between the end of the respective flange spring windows 16 and the opposed friction carrier spring windows 17. As the carrier 14 rotates around the hub 11 and flange 12 some friction hysterises will now be generated by the spacer 44 and the carrier plate 18 under the bias of the spring washers 27 & 29. The friction facing carrier 14 continues its relative anti-clockwise movement until the stop pins 21 abut the ends of the stop pin apertures as is well know in the trade.
If the load on the facings 24 is now relieved the facing carrier 14 now moves clockwise relative to the hub 11 until the carrier and hub flange 12 return to their "at rest" condition. The springs 60 ensure that the hub flange 12 is centered with respect to the hub 11.
When the driven plate goes into the over-run mode, the friciton facing carrier 14 now moves clockwise relative to the hub, the lost motion clearances in the clockwise direction are the same as for the other direction of rotation and therefore the same sequences of events takes place as for the drive mode of operation.
The manner of operation of the driven plate can be altered by delaying the operating clearances in the over-run mode as compared with the drive mode.
Now with reference to Fig. 5, there is illustrated a slightly modified clutch driven plate in which the hub flange 12 is rotationally fast with the hub 11.
The male plate 40 is made rotationally fast with the hub 11 by tabs 71 engaging with teeth 62 thereon and the female plate 41 is made rotationally fast with retainer plate 19 by tabs 70 so that the viscous damper 50 is operational for the whole rotational movement of the friction facing carrier 14 around the hub 11.
In Fig. 6 there is shown yet a further modification which is illustrated with reference to the embodiment of Fig. 5 but could be used in conjunction with the embodiment of
Figs. 1 to 4. The male and female plates 40 and 41 of the viscous damper are formed with a series of interdigitated annular ribs thereon. As previously described the male plate has two radially spaced inner and outer ribs 45 and 46 forming an annular chamber 51 having an intermeadiate annular rib 53 located therein between the two outer ribs. The female plate 41 has its two outer ribs 47 and 48 as previously described but with two radially spaced intermediate annular ribs 54 and 55 extending towards and located either side of the rib 53 on the male plate, so that the ribs 45, 46 and 53 on the male plate are interdigitated with the ribs 54 and 55 on the female plate 41. The viscous fluid is then sheared between opposed circular faces on the ribs.
A suitable fluid for use in the viscous damper mechanisms described above is a silicone fluid having a viscosity of between 80,000 and 200,000 centepoise.
Claims (11)
1. A friction clutch driven plate comprising a hub and a friction facing carrier mounted coaxially on the hub for limited rotational movement about the hub, and a damper operably located between the facing carrier and hub to resist said rotational movement, characterised in that said damper comprises two relatively rotatable parts arranged coaxially of the hub, one of said parts being rotatable with the hub, and the other of said parts being rotatable with facing carrier, and a viscous fluid is located in a chamber formed between said two parts so as to act therebetween as a viscous damper to oppose relative rotational movement between said two parts.
2. A friction clutch driven plate as claimed in Claim 1 wherein one of said rotatable parts comprises an annular plate having two radially spaced axially extending annular ribs thereon, and the other of said two rotatable parts is a second annular plate also having two radially spaced axially but oppositely extending ribs thereon, the oppositely extending ribs on the two plates providing pairs of annular sealing surfaces to define said chamber therebetween in which the viscous fluid is located.
3 A friction clutch driven plate as claimed in Claim 2, wherein the annular chamber is formed between the two annular ribs on said one annular plate to form a male plate, and the two annular ribs on the second annular plate are located one radially outwardly and one radially inwardly of the two ribs of said one plate and form a female plate.
4. A friction clutch driven plate as claimed in Claim 3 wherein on said male plate there are further provided a plurality of circumferential ribs that divide the chamber into circumferentially spaced arcuate cavities, and there are a like number of projecting paddle means on the female plate that are each located with play in a respective cavity, so that relative rotational movement between the two plate causes each paddle means to move in its respective cavity and cause the viscous fluid to flow therein.
5. A friction clutch driven plate as claimed in Claim 4 wherein cavities in the male plate are each interconnected, with the neighbouring cavities.
6. A friction clutch driven plate as claimed in Claim 3 wherein said female plate has two intermediate annular ribs thereon located between said inner and outer ribs, and the male plate has one intermediate annular rib located between its inner and outer ribs, said ribs on the male and female plates interdigitating , the viscous fluid being sheared between the circular opposed surfaces on said interdigitated ribs.
7. A friction clutch driven plate as claimed in any one of Claims 1 to 6 wherein there is further provided an annular hub flange projecting radially outwardly from the hub and one of said rotatable parts is fast with the facing carrier, and the other of the rotatable parts is rotationally fast with the hub so as to provide viscous damping over the whole phase of rotational movement of the facing carrier around the hub.
8. A friction clutch driven plate as claimed in any one of claims 1 to 6 wherein there is further provided an annular hub flange which'is mounted coaxially on the hub and is capable of limited angular rotation relative to the hub, and one of said rotatable parts is fast with the hub flange and the other of said rotatable parts is fast with the hub ,so as to provide viscous damping only during the period of rotation of the hub flange relative to the hub.
9. A friction clutch driven plate as claimed in Claim 8 wherein the hub flange has teeth on its inner periphery that mesh with teeth on the outer periphery of the hub, and the said one rotatable part has at least one axial projection that is engagable by said hub flange teeth to cause rotation of the one rotatable part relative to the second rotatable part.
10. A friction clutch driven plate as claimed in Claim 8 or Claim 9 wherein there are leaf springs operable between the hub flange and the hub to return the hub flange to an "at rest" position relative to the hub.
11. A friction driven plate substantially as described herein and as illustrated in the accompanying drawings.
11. A friction clutch driven plate as claimed in any one of Claims 1 to 10 , wherein the viscous fluid is a silicone fluid with a viscosity of between 80,000 and 200,000 centepoise.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB8919878A GB2235749B (en) | 1989-09-02 | 1989-09-02 | Friction clutch driven plates |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB8919878A GB2235749B (en) | 1989-09-02 | 1989-09-02 | Friction clutch driven plates |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| GB8919878D0 GB8919878D0 (en) | 1989-10-18 |
| GB2235749A true GB2235749A (en) | 1991-03-13 |
| GB2235749B GB2235749B (en) | 1993-07-28 |
Family
ID=10662448
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB8919878A Expired - Fee Related GB2235749B (en) | 1989-09-02 | 1989-09-02 | Friction clutch driven plates |
Country Status (1)
| Country | Link |
|---|---|
| GB (1) | GB2235749B (en) |
Cited By (23)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1995031653A1 (en) * | 1994-05-17 | 1995-11-23 | Automotive Products (Italia) S.P.A. | Friction clutch driven plates |
| GB2294995A (en) * | 1994-05-17 | 1996-05-15 | Automotive Prod Co Ltd | Friction clutch driven plates |
| EP0955485A3 (en) * | 1998-05-08 | 2002-02-13 | Ellergon Antriebstechnik GmbH | Torsional vibration damper, torsionally elastic and vibration damping coupling |
| WO2016050593A1 (en) * | 2014-10-01 | 2016-04-07 | Valeo Embrayages | Damper, in particular for a motor vehicle clutch |
| US9822862B2 (en) | 2015-10-02 | 2017-11-21 | Valeo Embrayages | Hydrokinetic torque coupling device for a motor vehicle |
| US9850995B2 (en) | 2015-10-02 | 2017-12-26 | Valeo Embrayages | Hydrokinetic torque coupling device for a motor vehicle |
| US9885406B2 (en) | 2015-10-02 | 2018-02-06 | Valeo Embrayages | Hydrokinetic torque coupling device for a motor vehicle |
| US9903456B1 (en) | 2016-08-24 | 2018-02-27 | Valeo Embrayages | Torque converter with lock-up clutch bias spring |
| US9989135B2 (en) | 2015-10-02 | 2018-06-05 | Valeo Embrayages | Hydrokinetic torque coupling device for a motor vehicle |
| US10030753B2 (en) | 2015-10-02 | 2018-07-24 | Valeo Embrayages | Hydrokinetic torque coupling device for a motor vehicle |
| US10054209B2 (en) | 2016-06-20 | 2018-08-21 | Valeo Embrayages | Torque transmitting device |
| US10094460B1 (en) | 2017-04-06 | 2018-10-09 | Valeo Embrayages | Vibration damper and lock-up clutch for hydrokinetic torque-coupling device, and method for making the same |
| US10094458B2 (en) | 2016-08-24 | 2018-10-09 | Valeo Embrayages | Torque transmitting device |
| US10100909B2 (en) | 2016-06-21 | 2018-10-16 | Valeo Embrayages | Torque transmission device for motor vehicle |
| US10107372B2 (en) | 2016-11-22 | 2018-10-23 | Valeo Embrayages | Torsional vibration damper and lock-up clutch for hydrokinetic torque-coupling device, and method for making the same |
| US10113624B2 (en) | 2016-11-17 | 2018-10-30 | Valeo Embrayages | Torsional vibration damper and lock-up clutch for hydrokinetic torque-coupling device, and method for making the same |
| US10151354B2 (en) * | 2016-09-09 | 2018-12-11 | Schaeffler Technologies AG & Co. KG | Universal damper and interchangeable hub assembly |
| US10161492B2 (en) | 2015-10-02 | 2018-12-25 | Valeo Embrayages | Hydrokinetic torque coupling device for motor vehicle |
| US10234007B2 (en) | 2016-05-23 | 2019-03-19 | Valeo Embrayages | Hydrokinetic torque coupling device for motor vehicle |
| US10288144B2 (en) | 2016-02-11 | 2019-05-14 | Valeo Embrayages | Transmission torque converter device |
| US10309482B2 (en) | 2014-08-08 | 2019-06-04 | Valeo Embrayages | Damper for an automobile clutch |
| US10400825B2 (en) | 2012-12-21 | 2019-09-03 | Valeo Embrayages | Vibration damper for a torque transmission device of a motor vehicle |
| US11448265B2 (en) * | 2018-12-11 | 2022-09-20 | Neapco Intellectual Property Holdings, Llc | Vehicle driveline joint including a vent and seal assembly |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB637257A (en) * | 1940-01-29 | 1950-05-17 | Dana Corp | Improvements in or relating to a clutch plate |
| GB2103335A (en) * | 1981-07-31 | 1983-02-16 | Sachs Systemtechnik Gmbh | Torsional vibration damper |
| GB2103336A (en) * | 1981-07-31 | 1983-02-16 | Sachs Systemtechnik Gmbh | Torsional vibration damper with laterally displaceable damping element |
| US4565273A (en) * | 1982-08-31 | 1986-01-21 | Kabushiki Kaisha Daikin Seisakusho | Damper disk having hydraulic shock absorbers |
| GB2197050A (en) * | 1986-11-03 | 1988-05-11 | Uni Cardan Ag | Clutch plate with viscous torsional damping |
-
1989
- 1989-09-02 GB GB8919878A patent/GB2235749B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB637257A (en) * | 1940-01-29 | 1950-05-17 | Dana Corp | Improvements in or relating to a clutch plate |
| GB2103335A (en) * | 1981-07-31 | 1983-02-16 | Sachs Systemtechnik Gmbh | Torsional vibration damper |
| GB2103336A (en) * | 1981-07-31 | 1983-02-16 | Sachs Systemtechnik Gmbh | Torsional vibration damper with laterally displaceable damping element |
| US4565273A (en) * | 1982-08-31 | 1986-01-21 | Kabushiki Kaisha Daikin Seisakusho | Damper disk having hydraulic shock absorbers |
| GB2197050A (en) * | 1986-11-03 | 1988-05-11 | Uni Cardan Ag | Clutch plate with viscous torsional damping |
Cited By (25)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2294995A (en) * | 1994-05-17 | 1996-05-15 | Automotive Prod Co Ltd | Friction clutch driven plates |
| GB2294995B (en) * | 1994-05-17 | 1998-04-01 | Automotive Prod Co Ltd | Friction clutch driven plates |
| WO1995031653A1 (en) * | 1994-05-17 | 1995-11-23 | Automotive Products (Italia) S.P.A. | Friction clutch driven plates |
| EP0955485A3 (en) * | 1998-05-08 | 2002-02-13 | Ellergon Antriebstechnik GmbH | Torsional vibration damper, torsionally elastic and vibration damping coupling |
| US10400825B2 (en) | 2012-12-21 | 2019-09-03 | Valeo Embrayages | Vibration damper for a torque transmission device of a motor vehicle |
| US10309482B2 (en) | 2014-08-08 | 2019-06-04 | Valeo Embrayages | Damper for an automobile clutch |
| WO2016050593A1 (en) * | 2014-10-01 | 2016-04-07 | Valeo Embrayages | Damper, in particular for a motor vehicle clutch |
| FR3026800A1 (en) * | 2014-10-01 | 2016-04-08 | Valeo Embrayages | DAMPER, IN PARTICULAR FOR A CLUTCH OF A MOTOR VEHICLE |
| US9850995B2 (en) | 2015-10-02 | 2017-12-26 | Valeo Embrayages | Hydrokinetic torque coupling device for a motor vehicle |
| US9885406B2 (en) | 2015-10-02 | 2018-02-06 | Valeo Embrayages | Hydrokinetic torque coupling device for a motor vehicle |
| US9822862B2 (en) | 2015-10-02 | 2017-11-21 | Valeo Embrayages | Hydrokinetic torque coupling device for a motor vehicle |
| US9989135B2 (en) | 2015-10-02 | 2018-06-05 | Valeo Embrayages | Hydrokinetic torque coupling device for a motor vehicle |
| US10030753B2 (en) | 2015-10-02 | 2018-07-24 | Valeo Embrayages | Hydrokinetic torque coupling device for a motor vehicle |
| US10161492B2 (en) | 2015-10-02 | 2018-12-25 | Valeo Embrayages | Hydrokinetic torque coupling device for motor vehicle |
| US10288144B2 (en) | 2016-02-11 | 2019-05-14 | Valeo Embrayages | Transmission torque converter device |
| US10234007B2 (en) | 2016-05-23 | 2019-03-19 | Valeo Embrayages | Hydrokinetic torque coupling device for motor vehicle |
| US10054209B2 (en) | 2016-06-20 | 2018-08-21 | Valeo Embrayages | Torque transmitting device |
| US10100909B2 (en) | 2016-06-21 | 2018-10-16 | Valeo Embrayages | Torque transmission device for motor vehicle |
| US10094458B2 (en) | 2016-08-24 | 2018-10-09 | Valeo Embrayages | Torque transmitting device |
| US9903456B1 (en) | 2016-08-24 | 2018-02-27 | Valeo Embrayages | Torque converter with lock-up clutch bias spring |
| US10151354B2 (en) * | 2016-09-09 | 2018-12-11 | Schaeffler Technologies AG & Co. KG | Universal damper and interchangeable hub assembly |
| US10113624B2 (en) | 2016-11-17 | 2018-10-30 | Valeo Embrayages | Torsional vibration damper and lock-up clutch for hydrokinetic torque-coupling device, and method for making the same |
| US10107372B2 (en) | 2016-11-22 | 2018-10-23 | Valeo Embrayages | Torsional vibration damper and lock-up clutch for hydrokinetic torque-coupling device, and method for making the same |
| US10094460B1 (en) | 2017-04-06 | 2018-10-09 | Valeo Embrayages | Vibration damper and lock-up clutch for hydrokinetic torque-coupling device, and method for making the same |
| US11448265B2 (en) * | 2018-12-11 | 2022-09-20 | Neapco Intellectual Property Holdings, Llc | Vehicle driveline joint including a vent and seal assembly |
Also Published As
| Publication number | Publication date |
|---|---|
| GB2235749B (en) | 1993-07-28 |
| GB8919878D0 (en) | 1989-10-18 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| 732E | Amendments to the register in respect of changes of name or changes affecting rights (sect. 32/1977) | ||
| 732E | Amendments to the register in respect of changes of name or changes affecting rights (sect. 32/1977) | ||
| 732E | Amendments to the register in respect of changes of name or changes affecting rights (sect. 32/1977) | ||
| PCNP | Patent ceased through non-payment of renewal fee |
Effective date: 20020902 |