GB2169989A - Torsional vibration damper with rotation-rate-dependent friction device - Google Patents
Torsional vibration damper with rotation-rate-dependent friction device Download PDFInfo
- Publication number
- GB2169989A GB2169989A GB08601274A GB8601274A GB2169989A GB 2169989 A GB2169989 A GB 2169989A GB 08601274 A GB08601274 A GB 08601274A GB 8601274 A GB8601274 A GB 8601274A GB 2169989 A GB2169989 A GB 2169989A
- Authority
- GB
- United Kingdom
- Prior art keywords
- vibration damper
- torsional vibration
- friction device
- idling
- output part
- 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
- 230000001419 dependent effect Effects 0.000 title description 3
- 238000010276 construction Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000630 rising effect Effects 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
- F16F15/1202—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 the damping action being at least partially controlled by centrifugal masses
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
In a torsional vibration damper having an under-load system 1 and an idling system 12, the output part of the under-load system is connected with a common hub 8 through a toothing 6,7 with play in the circumferential direction corresponding to the range of action of the idling damper. Between the output part of the under-load system and the common hub an additional friction device 11 is provided having a relatively high friction value which can be brought into action in dependence upon the rotation rate through centrifugal weights above the idling rotation rate. This arrangement avoids the so-called load change knock which occurs when at high torque and at high degrees of irregularity the range of action of the idling damper is run through too fast. <IMAGE>
Description
SPECIFICATION
Torsional vibration damper with rotation-rate-dependent friction device effective in the torsion angle range of the idling system
The invention relates to a torsional vibration damper, especially for clutch discs of friction clutches, consisting inter alia of an input part provided with friction linings, an output part provided with an internal toothing, torsion springs of different spring rigidities arranged therebetween which generate a spring characteristic curve with at least one break, possibly a friction device which is effective at least in the steepest region of the spring characteristic curve, and a further friction device which is variable in dependence upon rotation rate.
A torsional vibration damper of the above-stated style of construction is known for example from
German Utility Model No. 7,724,653. In this known torsional vibration damper a friction device is provided which becomes effective after the travelling of a specific torsion angle and which sacrifices friction force or is completely disengaged in dependence upon the centrifugal force with increasing rotation rate.
It is the problem of the present invention, in torsional vibration dampers with angled spring characteristic curve, to suppress or diminish those noises which occur when changes of load occur with great torque peaks. In such operational conditions what are called load change knocks occur on the stop elements which are responsible for the coming into action of the individual spring stages.
More especially those stop elements which become effective between the flattest spring characteristic curve, for example for the idling range, and the next spring stage are here affected.
In accordance with the invention this problem is solved by the characteristic of the main claim. Due to the arrangement of a further friction device which is variable in rotation-rate-dependence and is effective only in the region of the flattest spring characteristic curve, it is possible to moderate the load change knock at least to such extent that it can no longer be perceived. It is advantageous here to control this additional friction device in rotation-rate-dependence in such a way that it becomes effective above a pre-determined rotation rate. This additional friction device will preferably come into action above the idling rotation rate.
The controlling of the additional friction device in accordance with the invention achieves the object that outside the idling rotation rate during load change the idling range cannot be run through suddenly, since in addition to the inherently flat spring characteristic curve the friction force of the additional friction device must be overcome.
Especially in torsional vibration dampers with separate under-load system and idling system, the use of the above-mentioned rotation-rate-dependent additional friction device is especially effective.
Especially advantageous examples of embodiment are laid down according to Sub-Claims 4 to 11.
By a flat spring characteristic curve there is to be understood a spring characteristic in which the spring force varies only slightly in dependence upon the relative angle of rotation between the input part and the output part of the torsional vibration damper. Accordingly the spring force varies more greatly in dependence upon the relative rotation angle in the case of a steeper spring characteristic curve.
The invention will next be explained in greater detail by reference to an example of embodiment.
Individually:
Figure 1 shows the longitudinal section through a torsional vibration damper with under-load system and idling system;
Figures 2 and 3 show a cross-section ll-ll and a longitudinal section Ill-Ill through the centrifugal force device for controlling the additional friction device, Figure 3 being shown in axial exploded representation.
Figure 1 shows a torsional vibration damper consisting essentially of the following parts:- The torsional vibration damper 1 for the under-load range, the torsional vibration damper 12 for the idling range and the additional friction device 11. The torsional vibration damper 1 for the under-load range consists of the friction lining 2 which are riveted fast to a cover plate 4. A second cover plate 3 is arranged at an axial distance from the cover plate 4 and connected fast in rotation therewith and kept spaced therefrom by connecting rivets 16. The parts 2, 3 and 4 are formed as torque input parts of the torsional vibration damper 1. As output part the hub disc 5 is provided between the two cover plates 3 and 4. In this case several torsion springs 9 are provided which engage both in windows of the hub disc 5 and in windows of the cover plates 3 and 4.These windows can be formed so that the torsion springs 9 are brought into action by stages.
The torsional vibration damper 12 for the idling range consists likewise of two cover plates 14 and 15 which are connected fast in rotation with one another and kept spaced by means of connecting rivets 17. In this case the cover plate 15 is connected fast in rotation with the hub disc 5. The two cover plates 14 and 15 form the input parts of the torsional vibration damper 12 for the idling range, and between the two parts 14 and 15 there is arranged a hub disc 18 which functions as output part of the idling vibration damper.
Torsion springs 13 for the idling range are again arranged in appropriate windows between the parts 14 and 15 on the one hand and 18 on the other. The hub disc 18 is firmly connected with a common hub 8. This common hub 8 has an appropriate internal toothing on its internal diameter for engagement in the gear shaft (not shown). The hub disc 5 has an internal toothing 6 on its internal circumference which engages with play in the circumferential direction in an external toothing 7 of the common hub 8. This play corresponds to the range of action of the torsional vibration damper 12 for idling. The torsional vibration damper 1 for operation under load comprises an ordinary friction device 10 consisting in the present case of two friction rings, a dished spring and a thrust ring.
This friction device 10 is effective only outside the range of action of the torsional vibration damper 12. The torsional vibration damper 12 can be equipped with its own friction device. The additional friction device 11 is arranged on the side of the torsional vibration damper 1 remote from the torsional vibration damper 12. It consists of the individual parts described below, reference also being made to Figures 2 and 3. A control plate 23 is arranged fixedly on the hub disc 5. It carries slots 26 and 27 distributed on the circumference in which centrifugal weights 19 and 20 respectively can shift in the radial direction.In the circumferential regions between the slots 26 and 27 an outwardly open U-shaped section is provided which serves to hold the worm spring 21, extending through corresponding grooves in the centrifugal weights 19 and 20, in such a way that the centrifugal weights are secured in the axial direction at least during the assembly operation and also can assume an exactly predetermined radially inner rest position. This rest position may be seen from
Figure 2. A further control plate 22 is arranged at an axial distance from the control plate 23, pointing away from the hub disc 5. This control plate 22 comprises slots 24 and 25 in its radially outer region which, in the assembled condition, can correspond in the radial direction with the slots 26 and 27 of the control plate 23.
Radially within the centrifugal weights 19 and 20 the control plate 22 is connected through the friction device 11 with the common hub 8. In the present case the friction device consists of two thrust rings 31 and 32 which are arranged fast in rotation but axially displaceably on the external toothing 7, also of a thrust ring 33 which is arranged loosely, a dished spring 29, a securing ring 30, an axial stop 28 and three friction rings 34. With this arrangement it is possible to generate a relatively higher friction moment. As may be seen from Figure 2 especially, two sets of centrifugal weights 19 and 20 are distributed over the circumference of the control plate 23 in such a way that the individual parts of each set are arranged for example staggered by 1200 from one another.In the present case the centrifugal weights 19 and 20 are staggered by about 45" in relation to one another. In this way the force is transmitted relatively uniformly by way of the centrifugal weights between the two control plates 22 and 23. The corresponding slots 24 and 25 in the control plate 22 are arranged in relation to the slots 26 and 27 and in relation to the centrifugal weights 19 and 20 in such a way that only in the end positions of the toothing play between the internal toothing 6 and the external toothing 7 1 that is at the maximum deflections of the torsion damper device 12 for idling I can a rotation-fast connection be produced through the centrifugal weights, which then in each case are radially outwardly displaceable, provided that the corresponding rotation rate for the displacement of the centrifugal weights is reached or exceeded.
The function of the torsional vibration damper according to Figures 1 to 3 is now as follows:- In idling operation the torsional vibration damper 1 for the under-load range will remain practically as a rigid unit and only the torsion springs 13 of the torsional vibration damper 12 for the idling range will be loaded. Thus a relative movement takes place between the torsional vibration damper 1 and the common hub 8, which movement is not greater than the play between the two toothings 6 and 7.
In this idling range the centrifugal weights 19 and 20 are held in their rest position as reproduced in all three Figures by the worm spring 21. With rising rotation rate the centrifugal weights 19 and 20 endeavour to shift radially outwards against the force of the worm spring 21. This shift can take place when one of the end positions between the two toothings 6 and 7 is reached. If for example the torsional vibration damper 1 according to Figure 2 is subjected to traction stress, the control plate 23 moves in the clockwise direction in relation to the control plate 22 which is imagined as held fast.As soon as the overlap of the slots 26 of the control plate 23 with the slots 24 of the control plate 22 is produced I which at the same time corresponds to abutment of the two toothings 6 and 7 in this direction of loading I the centrifugal weights 19 can shift radially outwards into the slots 24. In this way they connect the two control plates 23 and 22 fast in rotation with one another so that on a subsequent torque loading in the over-run direction the increased friction force of the friction device 11 becomes effective in the entire range of play between the two toothings 6 and 7. This increased friction force remains effective as long as a rotation rate above the idling rotation rate is acting upon the entire clutch disc.Starting from the middle position assumed in Figure 2, in which the idling damper 12 is situated in the rest position, naturally also in the case of torque loading in the over-run direction opposite to the clockwise direction and in the case of simultaneous exceeding of the idling rotation rate the case can occur where the second set of centrifugal weights 20 engages in the corresponding slots 25 of the control plate 22 and thus the same rotation-fast connection is produced between the hub disc 5 and the common hub 8 through the friction device 11.
Due to the bringing into action of a friction device with relatively high friction value in dependence upon rotation rate, in principle the function of the idling vibration damper is maintained, but in this range a high friction force has to be overcome.
The arrangement of the overlap of the two kinds of slot for the centrifugal weights between the two control plates in each case in the region of the maximum angular deflection of the idling vibration damper brings with it the advantage that the centrifugal weights can produce the rotation-fast connection between the two control plates without torque loading, since in these end positions the two toothings 6 and 7 are also situated in their end positions. The higher torque loading of the clutch disc involved with working rotation rates lying above the idling rotation rate and also the consequent greater irregularity can completely suppress the so-called load change knock in the construction as described. This load change knock now no longer occurs, since in running through the range of the idling vibration damper the high friction force of the additional friction device must be overcome. At the same time the function of the idling friction device is completely maintained within the idling rotation rate range, since here this additional friction device is disengaged.
Claims (12)
1. Torsional vibration damper, especially for clutch discs of friction clutches, consisting inter alia of an input part provided with friction linings, an output part provided with an internal toothing, torsion springs of different spring rigidities arranged therebetween which generate a spring characteristic curve with at least one break, possibly a friction device which is effective at least in the steepest region of the spring characteristic curve and a further friction device which is variable in dependence upon rotation rate, characterised in that the further friction device (11) is effective at least in the region of the flattest spring characteristic curve.
2. Torsional vibration damper according to
Claim 1, characterised in that the further friction device (11) is variable in dependence upon rotation rate in such a way that it is effective above a predetermined rotation rate.
3. Torsional vibration damper according to
Claims 1 and 2, characterised in that this further friction device (11) is effective preferably above the idling rotation rate.
4. Torsional vibration damper according to
Claims 1 to 3, in which an under-load system and an idling system are provided the output part of the under-load system engages with a toothing with play in the circumferential direction according to the range of effect of the idling system in a toothing of a common hub on which the output part of the idling system is fixedly arranged, while the output part of the under-load system is firmly connected with the input parts of the idling system, characterised in that the further friction device (11) is arranged between the output part (5) of the under-load system (1) and the common hub (8).
5. Torsional vibration damper according to
Claim 4, characterised in that the further friction device (11) is arranged on the side of the underload system (1) remote from the idling system (12).
6. Torsional vibration damper according to
Claim 5, characterised in that the friction device (11) consists inter alia of two mutually axially opposite control plates (22, 23) comprising radially extending slots (24, 25, 26, 27), where in one plate (23) the slots (26, 27) are arranged on a smaller mean diameter and locking elements (19, 20) are arranged radially displaceably against spring force (21) therein and in the other plate (22) radially extending slots (24, 25) are arranged on a larger mean diameter and the one control plate (23) is firmly connected with the output part (5) of the under-load system (1) and the other control plate (22) is connected through the friction device (11) with the common hub (8).
7. Torsional vibration damper according to
Claim 6, characterised in that in the two end positions of the output part (5) of the under-load system (1) in the external toothing (7) of the common hub (8) the radially extending slots (24 to 27) of the two control plates (22, 23) correspond.
8. Torsional vibration damper according to
Claim 7, characterised in that the other control plate (22) is clamped in between two thrust rings (31, 32) which are arranged fast in rotation in the external toothing (7) of the common hub (8).
9. Torsional vibration damper according to
Claim 8, characterised in that the thrust ring (31) facing the output part (5) of the under-load system (1) is supported on an axial stop (28) of the external toothing (7).
10. Torsional vibration damper according to
Claim 7, characterised in that the locking elements (19, 20) are held in the rest position by a surrounding worm spring (21).
11. Torsional vibration damper according to
Claim 10, characterised in that two sets of locking elements (19, 20) are arranged in distribution on the circumference, of which the first set (19) in the drive direction and the second set (20) in the overrun direction correspond with corresponding slots (24, 25) in the other control plate (22).
12. Torsional vibration damper as claimed in claim 1, substantially as described herein with reference to and as illustrated by the accompanying drawings.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19853501466 DE3501466C2 (en) | 1985-01-18 | 1985-01-18 | Torsional vibration damper with a speed-dependent friction device that is effective in the torsion angle range of the idling system |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| GB8601274D0 GB8601274D0 (en) | 1986-02-26 |
| GB2169989A true GB2169989A (en) | 1986-07-23 |
| GB2169989B GB2169989B (en) | 1988-12-21 |
Family
ID=6260094
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB08601274A Expired GB2169989B (en) | 1985-01-18 | 1986-01-20 | Torsional vibration damper |
Country Status (3)
| Country | Link |
|---|---|
| DE (1) | DE3501466C2 (en) |
| FR (1) | FR2576377B1 (en) |
| GB (1) | GB2169989B (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2205383A (en) * | 1987-06-05 | 1988-12-07 | Fichtel & Sachs Ag | Clutch disc assembly |
| DE3805666A1 (en) * | 1988-02-24 | 1989-09-07 | Fichtel & Sachs Ag | Torsional vibration damper with friction dependent on the angle of rotation |
| FR2645231A1 (en) * | 1989-03-31 | 1990-10-05 | Valeo | TORSION DAMPER DEVICE, IN PARTICULAR CLUTCH FRICTION FOR MOTOR VEHICLES |
| GB2332036A (en) * | 1997-10-25 | 1999-06-09 | Mannesmann Sachs Ag | Torsional oscillation damper for vehicle clutches |
| DE19817907A1 (en) * | 1998-04-22 | 1999-10-28 | Rohs Voigt Patentverwertungsge | Friction disc damper |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0082595A1 (en) * | 1981-12-18 | 1983-06-29 | Borg-Warner Corporation | Vibration damper assembly for a clutch |
| GB2113351A (en) * | 1982-01-13 | 1983-08-03 | Automotive Products Plc | Friction clutch driven plate |
| EP0104823A1 (en) * | 1982-09-27 | 1984-04-04 | Borg-Warner Corporation | Multi-stage torsional damping device |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2361574A1 (en) * | 1976-08-09 | 1978-03-10 | Ferodo Sa | Friction clutch for automobile - has friction pads to inhibit large torsional oscillations by hysteresis |
| IT1128459B (en) * | 1979-01-23 | 1986-05-28 | Fichtel & Sachs Ag | ARRANGEMENT OF DAMPER OF TORSIONAL OSCILLATIONS PARTICULARLY FOR CLUTCHES IN MOTOR VEHICLES |
| DE2932531A1 (en) * | 1979-08-10 | 1981-02-26 | Luk Lamellen & Kupplungsbau | CLUTCH DISC |
-
1985
- 1985-01-18 DE DE19853501466 patent/DE3501466C2/en not_active Expired - Fee Related
-
1986
- 1986-01-17 FR FR8601122A patent/FR2576377B1/en not_active Expired
- 1986-01-20 GB GB08601274A patent/GB2169989B/en not_active Expired
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0082595A1 (en) * | 1981-12-18 | 1983-06-29 | Borg-Warner Corporation | Vibration damper assembly for a clutch |
| GB2113351A (en) * | 1982-01-13 | 1983-08-03 | Automotive Products Plc | Friction clutch driven plate |
| EP0104823A1 (en) * | 1982-09-27 | 1984-04-04 | Borg-Warner Corporation | Multi-stage torsional damping device |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2205383A (en) * | 1987-06-05 | 1988-12-07 | Fichtel & Sachs Ag | Clutch disc assembly |
| FR2616185A1 (en) * | 1987-06-05 | 1988-12-09 | Fichtel & Sachs Ag | CLUTCH DISC WITH DAMPING DEVICE CONTROLLED BY CENTRIFUGAL MASSES |
| GB2205383B (en) * | 1987-06-05 | 1991-04-03 | Fichtel & Sachs Ag | Clutch disc assembly |
| DE3805666A1 (en) * | 1988-02-24 | 1989-09-07 | Fichtel & Sachs Ag | Torsional vibration damper with friction dependent on the angle of rotation |
| DE3805666C2 (en) * | 1988-02-24 | 1998-06-04 | Mannesmann Sachs Ag | Torsional vibration damper with friction dependent on the angle of rotation |
| FR2645231A1 (en) * | 1989-03-31 | 1990-10-05 | Valeo | TORSION DAMPER DEVICE, IN PARTICULAR CLUTCH FRICTION FOR MOTOR VEHICLES |
| US5025904A (en) * | 1989-03-31 | 1991-06-25 | Valeo | Torsion damping device, in particular for a friction clutch for an automotive vehicle |
| GB2332036A (en) * | 1997-10-25 | 1999-06-09 | Mannesmann Sachs Ag | Torsional oscillation damper for vehicle clutches |
| GB2332036B (en) * | 1997-10-25 | 2002-02-06 | Mannesmann Sachs Ag | Torsional vibration damper for motor clutches |
| DE19817907A1 (en) * | 1998-04-22 | 1999-10-28 | Rohs Voigt Patentverwertungsge | Friction disc damper |
| US6299539B1 (en) | 1998-04-22 | 2001-10-09 | Rohs Voigt Patentverwertungs-Gesellschaft Mbh | Friction plate damper |
Also Published As
| Publication number | Publication date |
|---|---|
| GB2169989B (en) | 1988-12-21 |
| DE3501466A1 (en) | 1986-07-24 |
| FR2576377A1 (en) | 1986-07-25 |
| FR2576377B1 (en) | 1989-05-19 |
| DE3501466C2 (en) | 1994-10-06 |
| GB8601274D0 (en) | 1986-02-26 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PCNP | Patent ceased through non-payment of renewal fee |
Effective date: 20000120 |