GB2247065A - Clutch disk - Google Patents
Clutch disk Download PDFInfo
- Publication number
- GB2247065A GB2247065A GB9115864A GB9115864A GB2247065A GB 2247065 A GB2247065 A GB 2247065A GB 9115864 A GB9115864 A GB 9115864A GB 9115864 A GB9115864 A GB 9115864A GB 2247065 A GB2247065 A GB 2247065A
- Authority
- GB
- United Kingdom
- Prior art keywords
- disk
- hub
- annular spring
- friction
- covering
- 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
- 238000013016 damping Methods 0.000 claims abstract description 9
- 230000002093 peripheral effect Effects 0.000 claims description 4
- 230000008878 coupling Effects 0.000 claims description 2
- 238000010168 coupling process Methods 0.000 claims description 2
- 238000005859 coupling reaction Methods 0.000 claims description 2
- 238000000034 method Methods 0.000 claims 1
- 230000000284 resting effect Effects 0.000 description 3
- 239000000463 material Substances 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 239000002783 friction material Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
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
- F16F15/129—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
- F16F15/1292—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 characterised by arrangements for axially clamping or positioning or otherwise influencing the frictional plates
-
- 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
- F16F1/00—Springs
- F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
- F16F1/32—Belleville-type springs
- F16F1/328—Belleville-type springs with undulations, e.g. wavy springs
Abstract
The invention relates to a clutch disk for a friction clutch in which a friction arrangement (9 and 10 Fig 1) is arranged in addition to torsional damping springs (8). The friction arrangement comprises an axially corrugated annular spring 9 which is flattened in a plane manner in the region of the axial crests and troughs 11-16 of the corrugations. <IMAGE>
Description
f- c - 1 CLUTCH DISK The invention relates to a clutch disk assembly for a
friction clutch having an input member in the form of a lining carrier, an output member in the form of a hub as well as torsion springs arranged for resilient rotation under torque loading and a friction arrangement comprising at least one axially corrugated annular spring which is arranged between axially opposed friction faces and is axially pretensioned.
A clutch disk assembly of the above-mentioned design is known, for example, from German Offenlegungsschrift 32 28 515. In this known clutch disk there are used axially corrugated annular springs which experience high material wear owing to the small contact regions relative to their friction partners, and the frictional force is therefore subject to marked variations over the life span of the clutch disk.
An object of the invention is therefore to provide a simple and durable friction arrangement in conjunction with annular springs.
According to the invention there is provided a clutch disk assembly for a friction clutch comprising an input member in the form of a lining carrier, an output member in the form of a hub, several damping springs torsionally elastically coupling the output member to the input member, a friction arrangement, acting between the input member and output member, with friction faces which rest on one another in the axial direction of the hub and are pretensioned axially against one another by an annular spring which is axially corrugated to form peripherally alternating crests and troughs, characterised in that the crests and troughs of the annular spring have plane vertex regions extending in planes perpend- icularly to the axial direction.
Owing to the flattening of the vertex regions and therefore owing to the plane design of the rubbing regions of the annular spring parallel to the friction faces of the - 2 corresponding friction partner, area contact is produced which is subject to slighter wear and therefore produces uniform frictional forces over a longer period of time.
Thus the annular spring is preferably arranged between covering disk and hub disk. When using a control disk, moreover, the annular spring is advantageously arranged between a supporting disk and the control disk. A particularly compact design can be achieved in this way if the annular spring has a greater internal diameter than the external diameter of the covering disk-side friction ring, the supporting disk is bend radially outside the friction ring axially in the direction of the hub disk and penetrates there into a correspnnding recess in the hub disk. The annular spring is guided radially in a particularly simple manner on the step shaped by the bend of the supporting disk. The flattened regions of the annular spring have a peripheral dimension of about 1.5% of the annular spring.
The invention will now be described in more detail hereinafter with reference to the accompanying drawings in which:
FIGURE 1 is a section through the upper half of a clutch disk, FIGURE 2 is a side view of an annular spring, FIGURE 3 is a view of the annular spring radially from the exterior, and i 1 i i 7 1 FIGURE 4 is an enlarged section through the supporting disk.
Figure 1 shows the general installation with reference to a clutch disk assembly 1 arranged concentrically round an axis of rotation 7. The clutch disk 1 comprises a hub 5 for the non-rotatable positioning onto a gearshaft, the hub 5 being designed radially outwardly integrally with a hub disk 6. On both sides of the hub disk 6 there are arranged a lining 1 :n j i 1 i i i 3 carrier 2... as a covering disk and a disk-shaped covering plate 3 which are non-rotatably connected to one another in a known manner via rivet elements and are kept apart. The lining carrier 2 is connected to friction linings 4 via carrier plates. Damping springs 8 which allow resilient transmission of torque when the clutch disk 1 is loaded with torque are arranged in apertures in the hub disk 6 and in apertures of lining carrier 2 and covering plate 3. This allows a relative rotation between the hub disk 6 and lining carrier/covering plate, which is damped by a friction arrangement. In the present example, the friction arrangement comprises two friction rings 10 arranged on either side of the hub disk 6 on a cylindrical projection of the hub 5. One friction ring 10 is axially clamped between the hub disk 6 and the lining carrier 2 and the other friction ring 10 between the hub disk 6 and a disk-shaped supporting plate 18 which is connected non-rotatably but axially movably to the covering plate 3 via axially angled flaps 20 and which, in a diametral region greater than the diametral region of the friction ring 10, is axially loaded by an annular spring 9 resting, on the other hand, on the radially inner region of a disk-shaped control disk 17 which, in turn, rests on the interior of the covering plate 3. Owing to the axial initial tension of the annular spring 9, the annular spring 9 rests, on the one hand, on the axially opposed regions of supporting plate 18 and control plate 17. On the other hand, this axial clamping of the annular spring 9 simultaneously produces frictional contact between the supporting plate 18 and the hubdisk 6 with interposition of a friction ring 10 and between the hub disk 6 and the lining carrier 2, also with interposition of a friction ring 10.
This friction arrangement operates briefly as follows: in the event of torque loading and relative rotation between lining carrier 2 and covering plate 3, on the one hand, and the hub disk 6, on the other hand, a frictional force is 1 X 4 invariably produced by the friction rings 10. Selection of the friction material of the friction rings 10 ensures that this frictional force is kept at a relatively low level. The control plate 17 co-operates in the normal manner with a set of damping springs 8 which come into play only after a certain angle of rotation has been covered. The control plate 17 is thus secured relative to the hub disk by damping springs in its position after exceeding this angle, an additional frictional force being produced in that the supporting plate 18 rotates together with the covering plate 3 relative to the control plate 17. This additional frictional force is used intentionally with greater angles of rotation. A higher frictional value is also simultaneously available owing to the metal on metal friction. The enlarged illustration of the supporting plate according to Figure 4 shows that the annular spring 9 is used between the friction face 23 of the supporting plate 18 and the friction face 24 of the covering plate 3. If the supporting plate 18 and covering plate 3 are of the same material, relative movement is possible between the annular spring 9 both on the friction face 23 and on the friction face 24. In order to have minimum wear at these points, the annular spring 9 is constructed according to Figures 2 and 3. The vertex regions 11, 13 and 15, resting on one friction face, of the crests and troughs of the corrugations as well as the vertex regions 12, 14 and 16 resting on the opposing friction face are flattened in a plane manner and therefore extend in parallel with the corresponding friction faces 23 and 24 and in planes which are normal to the axis. The peripheral boundaries of these regions 11 to 16 can extend parallel to one another in each case or also at an angle extending through the axis of rotation 7 according to Figure 2. These regions peripherally cover about 1.5% of the total central periphery of the annular spring 9.
The arrangement of the annular spring 9 in the clutch 1 i 1 1.
disk 1 is particularly compact according to Figures 1 and 4 since the annular spring has a greater internal diameter than the external diameter of the friction rings 10 and therefore comes to rest radially inside the region between the friction rings 10 and the torsion springs 8. On the other hand, the supporting plate 18 is bent radially outside the friction ring 10 axially in the direction of the hub disk 6 and extends there in a recess 19 in this hub disk 6. It is therefore possible to offset the friction face 23 on the supporting plate 18 axially toward the hub disk 6 and to utilise the available space to an optimum. At the same time, the step 22 produced by the bend of the supporting plate is used to fix the annular spring 9 in the radial direction. The supporting plate 18 is peripherally guided but axially movably held in corresponding openings 21 in the covering plate 3 by the flaps 20 which are set out axially on its internal diameter.
li:I i -- 1 6
Claims (8)
1. Clutch disk assembly for a friction clutch comprising an input member in the form of a lining carrier (2), an output member in the form of a hub (5), several damping springs torsionally elastically coupling the output member to the input member, a friction arrangement, acting between input member and output member, with friction faces (10, 23, 24) which rest on one another in the axial direction of the hub and are pretensioned axially against one another by an annular spring (9) which is axially corrugated to form peripherally alternating crests and troughs, characterised in that the crests and troughs of the annular spring (9) have plane vertex regions (11 - 16) extending in planes perpendicularly to the axial direction.
2. Clutch disk assembly according to claim 1, characterised in that the hub (5) is connected integrally to a hub disk (6), in that covering disks (2, 3) which are non-rotatably connected to one another and are held apart are arranged axially on both sides of the hub disk (6), a first covering disk (2) forming the lining carrier, the damping springs (8) being arranged in apertures in the hub disk (6) on the one hand and the covering disks (2, 3) on the other hand, and in that the annular spring (9) is arranged between one (3) of the covering disks (2, 3) and the hub disk (6) and first friction faces (10) pretensioned against one another by means of the annular spring (9) are provided between the other covering disk (3), in particular the first covering disk and the hub disk (6).
3. Clutch disk assembly accordifig to claim 1 or 2, characterised in that the hub (5) is connected integrally to a hub disk (6), in that axially on both sides of the hub disk (6) there are arranged covering disks (2, 3) which are non-rotatably connected to one another and are held apart, the first (2) of 1 l! 1 i i i i i i i 1 : i 1 1 1 1 1 1;1 1, v 7 which forms the lining carrier, the damping springs (8) being arranged in apertures in the hub disk (6) on the one hand and the covering disks (2, 3) on the other hand, and in that a supporting disk (18) as well as a control disk (17) are arranged axially between the hub disk (6) and one (3) of the covering disks (2, 3), in particular the second of the two covering disks, wherein the supporting disk (18) is arranged radially between the hub (5) and the damping springs (8), is non-rotatably but axially movably coupled to this one covering disk (3) and is supported on the hub disk via second friction faces (10) and wherein the control disk (17) is coupled with rotational clearance to the output member, is connected to this one covering disk via third friction faces (23, 24) and, with its radially inner region, radially overlaps the radially outer region of the supporting disk (18) on the side of the supporting disk (18) axially removed from the hub disk (6) and in that the annular spring (9) is arranged axially between the radially inner region of the control disk (17) and the radially outer region of the supporting disk (18).
4. Clutch disk assembly according to claim 3, characterised in that the second friction faces are formed by a friction ring (10) and optionally also the first friction faces by a further friction ring (10), the external diameter at least of the friction ring (10) forming the second friction faces being smaller than the internal diameter of the annular spring (9) and in that the supporting disk (18) has an annular region (23) which is bent radially outside the friction ring (10) toward the hub disk and on which the annular spring (9) rests.
5. Clutch disk assembly according to claim 4, characterised in that the hub disk (6) has, on the side pointing toward the annular spring (9) radially outside the friction ring (10) a recess (19) which is concentric to the hub axis (7) and into 8 which the bent annular region (23) of the supporting disk (18) penetrates.
6. Clutch disk assembly according to claim 4 or 5, characterised in that the bent annular region of the supporting disk (18) forms a step (22) on which the annular spring (9) is radially guided.
7. Clutch disk assEmbly according to one of claim 1 to 6, characterised in that the plane vertex regions (11 - 16) of the annular spring (9) have a width in the peripheral direction of the annular spring (9) which is approximately 1.5% of the central peripheral length of the annular spring (9).
8. Clutch disk assembly as claimed in claim 1 substantially as described with reference to the accompany-ing drawings.
Published 1992 at The Patent Office. Concept House. Cardifr Road. Newport. Gwent NP9 IRH. Further copies ma ' be obtained froni Sales Branch. Unit 6. Nine Mile Point. Cwrnfelinfach. Cross Keys. Newport. NP I 7HZ. Printed ky Multiplex techniques lid. Si Mary Cray- Kent- 1 v 11 11 1 1 1 1 1 i 1 1 1
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4023716A DE4023716A1 (en) | 1990-07-26 | 1990-07-26 | CLUTCH DISC WITH A RING SPRING WITH PLANES |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| GB9115864D0 GB9115864D0 (en) | 1991-09-04 |
| GB2247065A true GB2247065A (en) | 1992-02-19 |
| GB2247065B GB2247065B (en) | 1994-09-21 |
Family
ID=6411034
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB9115864A Expired - Fee Related GB2247065B (en) | 1990-07-26 | 1991-07-23 | Clutch disk |
Country Status (5)
| Country | Link |
|---|---|
| BR (1) | BR9103164A (en) |
| DE (1) | DE4023716A1 (en) |
| FR (1) | FR2665232B1 (en) |
| GB (1) | GB2247065B (en) |
| IT (1) | IT1250209B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2298473A (en) * | 1995-03-01 | 1996-09-04 | Luk Lamellen & Kupplungsbau | Clutch disc with friction damping |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| ES2122823B1 (en) * | 1993-11-26 | 2000-02-01 | Fichtel & Sachs Ag | TORSION VIBRATION DAMPER IN THE DRIVE CHAIN OF AN AUTOMOBILE, WITH AXIAL TENSIONED FRICTION RING. |
| DE4442868A1 (en) * | 1994-12-02 | 1996-06-13 | Fichtel & Sachs Ag | Clutch disc with torsional vibration damper |
| DE4444177A1 (en) * | 1994-12-12 | 1996-06-20 | Fichtel & Sachs Ag | Vehicle clutch disc with torsional oscillation damper |
| DE19545070C2 (en) * | 1994-12-12 | 1998-05-28 | Mannesmann Sachs Ag | Clutch disc with dragged friction device |
| FR3059377B1 (en) * | 2016-11-30 | 2019-01-25 | Valeo Embrayages | PHASING DEVICE FOR FRICTION CLUTCH AND FRICTION CLUTCH DAMPER COMPRISING SUCH A DEVICE |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2093565A (en) * | 1981-02-25 | 1982-09-02 | Valeo | Torsion damping device for an automotive clutch plate assembly |
| GB2151749A (en) * | 1983-12-15 | 1985-07-24 | Fichtel & Sachs Ag | Clutch disc for a motor vehicle friction disc clutch |
| GB2184516A (en) * | 1985-12-16 | 1987-06-24 | Daikin Mfg Co Ltd | Radial positioning of a friction member in a damper disc |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BE487469A (en) * | 1946-08-06 | |||
| US2636363A (en) * | 1948-12-30 | 1953-04-28 | Borg Warner | Vibration dampener |
| DE1856794U (en) * | 1962-03-23 | 1962-08-16 | Christian Bauer K G | DISC SPRING. |
| DE3228515A1 (en) * | 1982-07-30 | 1984-02-02 | LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl | Clutch disc |
| JPS5943721U (en) * | 1982-09-16 | 1984-03-22 | 株式会社大金製作所 | damper disc |
| GB8619870D0 (en) * | 1986-08-15 | 1986-09-24 | Automotive Prod Plc | Friction clutch driven plate |
-
1990
- 1990-07-26 DE DE4023716A patent/DE4023716A1/en not_active Ceased
-
1991
- 1991-07-23 GB GB9115864A patent/GB2247065B/en not_active Expired - Fee Related
- 1991-07-24 FR FR9109625A patent/FR2665232B1/en not_active Expired - Fee Related
- 1991-07-24 BR BR919103164A patent/BR9103164A/en unknown
- 1991-07-25 IT ITTO910588A patent/IT1250209B/en active IP Right Grant
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2093565A (en) * | 1981-02-25 | 1982-09-02 | Valeo | Torsion damping device for an automotive clutch plate assembly |
| GB2151749A (en) * | 1983-12-15 | 1985-07-24 | Fichtel & Sachs Ag | Clutch disc for a motor vehicle friction disc clutch |
| GB2184516A (en) * | 1985-12-16 | 1987-06-24 | Daikin Mfg Co Ltd | Radial positioning of a friction member in a damper disc |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2298473A (en) * | 1995-03-01 | 1996-09-04 | Luk Lamellen & Kupplungsbau | Clutch disc with friction damping |
| GB2298473B (en) * | 1995-03-01 | 1999-03-17 | Luk Lamellen & Kupplungsbau | Damping apparatus |
Also Published As
| Publication number | Publication date |
|---|---|
| DE4023716A1 (en) | 1992-01-30 |
| BR9103164A (en) | 1992-02-11 |
| FR2665232B1 (en) | 1995-09-01 |
| ITTO910588A1 (en) | 1993-01-25 |
| ITTO910588A0 (en) | 1991-07-25 |
| GB9115864D0 (en) | 1991-09-04 |
| IT1250209B (en) | 1995-04-03 |
| FR2665232A1 (en) | 1992-01-31 |
| GB2247065B (en) | 1994-09-21 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PCNP | Patent ceased through non-payment of renewal fee |
Effective date: 20040723 |