GB2170882A - Torsional vibration damper - Google Patents

Torsional vibration damper Download PDF

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Publication number
GB2170882A
GB2170882A GB08601543A GB8601543A GB2170882A GB 2170882 A GB2170882 A GB 2170882A GB 08601543 A GB08601543 A GB 08601543A GB 8601543 A GB8601543 A GB 8601543A GB 2170882 A GB2170882 A GB 2170882A
Authority
GB
United Kingdom
Prior art keywords
piston
hydraulic cylinder
torsional vibration
vibration damper
axially
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.)
Withdrawn
Application number
GB08601543A
Other versions
GB8601543D0 (en
Inventor
Alfred Schraut
Joachim Nittke
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF Sachs AG
Original Assignee
Fichtel and Sachs AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Fichtel and Sachs AG filed Critical Fichtel and Sachs AG
Publication of GB8601543D0 publication Critical patent/GB8601543D0/en
Publication of GB2170882A publication Critical patent/GB2170882A/en
Withdrawn legal-status Critical Current

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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
    • F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
    • F16F15/161—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material characterised by the fluid damping devices, e.g. passages, orifices
    • 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
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/60—Clutching elements
    • F16D13/64—Clutch-plates; Clutch-lamellae
    • F16D13/68—Attachments of plates or lamellae to their supports
    • 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
    • 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
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
    • F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
    • F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
    • F16F9/20—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein with the piston-rod extending through both ends of the cylinder, e.g. constant-volume dampers

Abstract

In a torsional vibration damper comprising a disc part 7 and two connected side discs (9) arranged on axially opposite sides of the disc part (7) which are rotatable in relation to the disc part (7) and have windows (21) lying approximately axially opposite to windows (25) of the disc part (7) containing spring elements (23), in further windows (25, 29) of the disc part (7) and of the side discs (9) there is arranged at least one hydraulic damper element which is effective in the relative rotation between the disc part (7) and the side discs (9) and comprises a hydraulic cylinder (33), a piston (37) displaceable in the hydraulic cylinder (33) and dividing the latter into two pressure chambers (39, 41) and a constricted passage (43) connecting the chambers. The hydraulic cylinder (33) is supported between edges (49), of the windows (29) of the two side discs (9). The piston (37) has a piston rod (45) emerging at both axial ends from the hydraulic cylinder (33) and supported on edges (47), of the window (25) of the disc part (7). In addition the hydraulic cylinder (33) can contain springs (51) on which the piston (37) abuts after travelling through a predetermined relative rotation angle range, for the obtaining of an angled spring characteristic curve of the torsional vibration damper. <IMAGE>

Description

SPECIFICATION Torsional vibration damper The invention relates to a torsional vibration damper for the drive line especially of a motor vehicle and specially for a clutch disc or a divided fly-wheel having several intertia masses rotatable in relation to one another.
From Fed. German Publication Specification No. 3,323,299 a clutch disc for a motor vehicle friction clutch is known on whose hub, which is to be coupled fast in rotation with the gear input shaft, a drive disc provided with clutch friction linings is rotatably mounted. The hub carries a radially protruding flange which is coupled rotationally elastically with the drive disc through a plurslity of hydraulic damper elements. Each of the damper elements comprises a hydraulic cylinder in which a piston is displaceably arranged which divides the hydraulic cylinder into two pressure chambers. The pressure chambers are filled with hydraulic fluid and connected with one another through a passage having a constriction.In both pressure chambers there are seated helical compression springs which ensure an elastic connection of the hydraulic cylinder with the piston, The hydraulic cylinder for one part and the piston rod for the other part, which is conducted axially on one side out of the cylinder, are connected each through joints with the hub flange and the drive disc.
It is the problem of the invention to simplify the construction of the torsional vibration damper. More eapecially the hydraulic damper elements are to be of such configuration that in the case of conventional clutch discs and divided fly-wheels of motor vehicle friction clutches they can be used without substantial design modifications of the clutch components.
The hydraulic damper element used within the scope of the invention comprises a hydraulic cylinder which is divided into two pressure chambers by a piston displaceable in the hydraulic cylinder. A constricted passage renders possible a pressure equalisation of the hydraulic fluid contained in the pressure chambers, in the case of a relative displacement of the piston and the hydraulic cylinder. The piston has a piston rod which emerges axially at both ends from the hydraulic cylinder. Such a hydraulic damper element, in the case of conventional torsional vibration dampers with disc parts or side discs rotatable in relation to one another in windows, can be installed substantially without design modifications of these parts, in place of the springs used hitherto for rotationally elastic coupling.In this case the ends of the piston rod and of the hydraulic cylinder are subject to the loading of the window edges facing one another in the circumferential direction. The hydraulic cylinders can contain additional springs on which the pistons abut, so that torsional vibration dampers can be assembled with angled spring characteristic curve.
Examples of embodiment of the invention are to be explained in greater detail by reference to drawings, wherein: FIGURE 1 shows a diagrammatic axial longitudinal section through the upper half of a clutch disc of a motor vehicle friction clutch; FIGURE 2 shows a partial axial cross-section through the clutch disc, seen along a line Il-Il in Figure 1 and FIGURES 3 to 5 show variants of a hydraulic damper element usable in the clutch disc according to Figures 1 and 2.
Figures 1 and 2 show a clutch disc 1 of a motor vehicle friction clutch having a hub 1 which is coupled in the usual way fast in rotation but axially displaceably through an internal toothing 3 with an input shaft (not further illustrated) of a motor vehicle gearing, which shaft is in rotation about a rotation axis 5.
The hub 1 carries fast in rotation a substantially radially protruding hub disc 7. Axially on both sides of the hub disc 7 there are arranged side discs 9, 11 which are firmly connected with one another by means of distance rivets 13 or the like. The side discs 9, 11 annularly enclose the hub 1 and are rotatable in relation thereto through a limited angle of rotation about the rotation axis 5. One of the side discs, here the side-disc 11, is provided with clutch friction linings 15. In several windows 21 of the hub disc 7 which are distributed in the circumferential direction on a circle about the rotation axis 5 there are seated helical springs 23 stressable in the circumferential direction, which engage in windows of the side discs 9, 11 which are axially opposite to the windows 21.The springs 23 are resiliently stressed in the relative rotation of the hub disc 7 for one part and of the side discs 9, 11 for the other, and couple the side discs 9, 11 and thus the clutch friction linings 1 5 rotationally elastically with the hub disc 7 and thus the hub 1.
In addition to the windows 21, further windows 25 are provided lying diametrically opposite to one another in the hub disc 7. In the windows 25 there are seated hydraulic damper elements 27, explained in greater detail below, which protrude in the axial direction beyond the hub disc 7 and engage in axially opposite windows 29, 31 of the two side discs 9, 11. The damper elements 27 are loaded in both directions of rotation in the relative rotation of the side discs 9, 11 and of the hub disc 7, and damp the rotational vibrations between these parts.
Each of the two damper elements 27 comprises a tubular hydraulic cylinder 33, the ends of which are closed by screwed-in end lids 35 of annular disc form. A piston 37 is arrsnged axially displaceably in the hydraulic cylinder 33, the cylinder axis of which extends tangentially to a circle centred on the axis 5 of rotation. The piston 37 divides the hydraulic cylinder 33 into two pressure chambers 39, 41 which are connected with one another by a constricted passage 43 between the circumference of the piston 37 and the inner peripheral surface of the cylinder. The piston 37 has a piston rod 45 issuing in sealed manner axi slly at both ends through the end lids 35 and held in the circumferential direction between edges 47, directed towards one another in the circumferential direction, of the window 25 of the hub disc 7.The hydraulic cylinder 33 for its part abuts with its end lids 35 on edges 49, directed towards one another in the circumferential direction, of the windows 29 and 31 of the side discs 9, 11 respectively. In the relative rotation of the side discs 9, 11 and of the hub disc 7 the piston 37 is displaced in relation to the hydraulic cylinder 33, whereby the hydraulic fluid contained in the pressure chambers 39, 41 is forced from one pressure chamber into the other by way of the constricted passage 43, and damps the rotating movement of the side discs 9, 11 in relation to the hub disc 9.
Axially on both sides of the piston 37 in the hydraulic cylinder 33 there are arranged dished spring packs 51 which are supported under initial stress on their side remote from the piston 37 on end faces 53 of the end lids 35 and on their side facing the piston 37 in each case through a support washer 55 on annular shoulders 57, facing axially away from one another, of the hydraulic cylinder. The stop washers 55 are movable axially towards the end lids 35 against the force of the dished spring packs 51 and form stops for the piston 37, between which the piston 37 can move within a limited relative rotation angle range of the hub disc 7 and the side discs 9, 11, without loading the dished spring packs 51.
On exceeding of the relative rotation angle range the dished spring packs 51 are resiliently stressed in addition to the springs 23, which corresponds to an angled spring characteristic curve of the torsional vibration damper.
The piston rod 45 is protected against soiling by elastic sleeves 59 opposite to the end lids 35. Although Figure 2 shows only two damper elements 27, a different number of such elements can also be used. Furthermore the idle motions of the pistons between the two resilient end stops can be different from one damper element to another.
Variants of hydraulic damper elements are to be explained below, which can be used in place of the damper element 27 in a clutch disc according to Figures 1 and 2. Figure 3 shows a hydraulic damper element 101 with a hydraulic cylinder 103 which again is divided by an axially displaceable piston 105 into two pressure chambers 107, 109. A constricted passage 111 of annular gap form between the external circumference of the piston 105 and the internal peripheral surface 113 of the hydraulic cylinder 103 interconnects the two hy draulic fluid-filled pressure chambers 107, 109. The damper element 101 differs from the damper element 27 essentially only in the axially varying dimensioning of the constricted passage 111. The inner peripheral surface 113 of the hydraulic cylinder 103 has a barrelshaped contour and an internal diameter decreasing axially outwards.Thus the constricted passage 111 narrows towards the axially outer end positions of the piston 105, so that the damping effect increases progressively towards the end positions.
Figure 4 shows a hydraulic damper element 201 which differs from the damper element 27 essentially only in that in its hydraulic cylinder 203 an annular piston 209 is axially displaceably arranged in addition to the piston 207 which is loadable through its piston rod 205. The annular piston 209 surrounds the piston 207, forming a constricted passage 211, and extends with its axially opposite end faces 213, 215 into the two pressure chambers 217, 219 which the piston 207 axially separates in the hydraulic cylinder 203. Axially on both sides of the piston 207 there are again arranged dished spring pscks 221 corresponding to the dished spring packs 51, on which the piston 207 can abut through axially movable support washers 223, similar to the support washers 55.The annular piston 209 is resiliently fixed in both directions on the support washers 223 axially on both sides by axially acting corrugated springs 225. In the case of comparatively slow relative movement between the piston 207 and the hydraulic cylinder 203 the hydraulic fluid can escape from one pressure chamber into the other by way of the constricted passage 211.In the case of quick relative displacements the pressure increase in the one pressure chamber however effects a displacement of the annular piston against the force of the corrugated spring towards the other pressure chamber, which corresponds to a virtual enlargement of the constricted passage and reduces the impact loading of the damper element, Figure 5 shows a hydraulic damper element 301 with two mutually separate, coaxially arranged hydraulic cylinders 303 and 305 in each of which a piston 307 and 309 is axially displaceable. The pistons 307, 309 are rigidly connected with one another by a common piston rod 311 and divide the hydraulic cylinders 303 and 305 each into two pressure chambers 313 and 315. The pressure chambers 313 and 315 filled with hydraulic fluid are connected with one another through annular constricted passages 317, 319 at the circumferences of the pistons 307, 309.
A dished spring pack 323 is guided axially displaceably on the piston rod 311 by means of a guide ring 321 axially between the hy draulic cylinders 303, 305, which are displaceable in relation to one another along the piston rod 311. A spring housing 325, which encloses the dished spring pack 323, ensures an initial stressing of the dished spring pack 323. The hydraulic cylinders 303, 305 are closed by end lids 327, 329 on their side axially adjacent to the dished spring pack 323, and are supported with annular extension pieces 331, 333 on opposite sides axially resiliently on the dished spring pack 323.
In each of the hydraulic cylinders 303,305 a further dished spring pack 335 and 337 is arranged axially between the end lid 327 and 329 and the associated piston 307 and 309 respectively and is axially supported between the end lid 327 and 329 for the one part and through a support washer 339 and 341 on the hydraulic cylinder 303 and 305 for the other part. The dished spring packs 335, 337 have equal spring characteristics different however from that of the dished spring pack 323. Thus the hydraulic damper element has a spring characteristic curve angled in two places.The manner of operation of the damper element-301 is as follows, it being assumed that the piston rod 311 supported on the hub disc of the clutch disc is held fast and the hydraulic cylinders 303, 305, supported on the side discs of the clutch disc, are displaced to the left by the window edges of the side discs acting on the hydraulic piston 303, in Figure 5. In the relative displacement the volume of the pressure chambers 313, 315 situated axially to the right in each case is reduced, the relative movement being damped, until the piston 309 abuts on the stop washer 341 and compresses the dished spring pack 337, provided that this is softer than the dished spring pack 323. Here the hydraulic cylinder 305 bears through the harder dished spring pack 323 on the hydraulic cylinder 303. With increasing relative displacement the dished spring pack 323 will subsequently also be compressed.If the dished spring pack 323 is softer than the dished spring pack 337, then firstly the dished spring psck 323 and then the dished spring pack 337 will be stressed. In a corresponding manner on a displacement of the hydraulic cylinders 303, 305 to the right in Figure 5 the dished spring packs 337 and 323 will be relaxed again, before the dished spring pack 335 and subsequently again the dished spring pack 323 is loaded.
The hydraulic damper elements were described above with reference to the clutch disc of a motor vehicle friction clutch. However the torsional vibration damper consisting of a hub disc and two side discs arranged axially beside the hub disc can also be used in a divided fly-wheel, consisting of two flywheel discs, of the friction clutch or the like.
It is understood that in place of the input part of the torsional vibration damper formed in Figure 1 by the side discs it is also possible for the hub disc to be used as input part, in which case accordingly the side discs form the output part of the damper.

Claims (17)

1. Torsional vibration damper comprising: a) a disc part (7) rotatable about a rotation axis (5) with several windows (25) arranged around the rotation axis (5), b) two side discs (9) arranged on axially opposite sides of the disc part (7) and connected fast in rotation with one another, which are rotatable about the rotation axis (5) in relation to the disc part (7) and have windows (29) lying approximately axially opposite to the windows (25) of the disc part (7), c) at least one spring element (23) arranged in axially opposite windows of the disc part (7) and of the side discs (9), which couples the disc part (7) and the side discs (9) rotationally elastically with one another, d) at least one hydraulic damper element (27; 101; 201; 301) effective in the relative rotation between the disc part (7) and the side discs (9), having a hydraulic cylinder (33; 103; 203; 303, 305), a piston (37; 105; 207; 307, 309) displaceable in the hydraulic cylinder and dividing the hydraulic cylinder into two pressure chambers (39, 41; 107, 109; 217, 219; 313; 315), the piston rod (45; 205; 311) of which piston issues in sealed manner from the hydraulic cylinder, and having a constricted passage (43; 111; 211; 317, 319) connecting the two pressure chambers with one another, characterised in that the hydraulic cylinder (33; 103; 203; 303, 305), with cylinder axis extending substantially tangentially to a circle about the rotation axis (5), is arranged in axially opposite windows (25, 29, 31) of the disc part (7) and of the side discs (9) and is supported in the direction of the cylinder axis on edges (49), facing one another in the circumferential direction, of the windows (29, 31) of the side discs (9), and in that the piston rod (45; 205; 311) emerges axially at both ends from the hydraulic cylinder (33; 103; 203; 303, 305) and is supported on edges (47), facing one another in the circumferential direction, of the window (25) of the disc part (9).
2. Torsional vibration damper according to Claim 1, characterised in that a spring element (51; 221; 335, 337) which is resilient in the direction of the cylinder axis is arranged in the hydraulic cylinder (33; 103; 203; 303, 305) on at least one axial side of the piston (37; 105; 207; 307, 309), which element is supported with its end remote from the piston on the hydraulic cylinder and comprises at its end nearer the piston a stop (55; 223; 339, 341) for the piston, in relation to which the piston is movable.
3. Torsional vibration damper according to Claim 2, characterised in that between the spring element (51; 221; 335, 337) and the piston (37; 105; 207; 307, 309) there is arranged a stop disc (55; 223; 339, 341) annularly enclosing the piston rod (45; 205; 311) and movable in the direction of the cylinder axis in relation to the piston rod and the hydraulic cylinder (33; 103; 203; 303, 305), by means of which stop disc the piston is supportable on the spring element.
4. Torsional vibration damper according to Claim 3, characterised in that the stop washer (55; 223; 339, 341) and the spring element (51; 221; 335, 337) are clamped in with initial stress between abutment faces (53, 57), directed axially towards one another, of the hydraulic cylinder (33; 103; 203; 303, 305).
5. Torsional vibration damper according to one of Claims 2 to 4, characterised in that the spring element (51; 221; 335, 337) is held between a stop shoulder (57) of the hydraulic cylinder (33; 103; 203; 303, 305) and an end lid (35; 327, 329) of the hydraulic cylinder which is secured to the hydraulic cylinder and encloses the piston rod (45; 205; 311).
6. Torsional vibration damper according to one of Claims 2 to 5, characterised in that the spring element is formed as dished spring pack (51; 221; 335, 337).
7. Torsional vibration damper according to one of Claims 2 to 6, characterised in that spring elements (51; 221) on which the piston is alternately supportable are provided axially on both sides of the piston (37; 105; 207).
8. Torsional vibration damper according to Claim 7, characterised in that an annular piston (209) enclosing the piston (207) is arranged axially between the spring elements (221) in the hydraulic cylinder (203), which annular piston is resiliently displaceable in relation to the piston (207) in the direction of the cylinder axis and with its mutually opposite axial end faces (213, 215) adjoins the two pressure chambers (217, 219).
9. Torsional vibration damper according to Claim 8, characterised in that the annular piston (209) is axially resiliently held axially between two further springs (225) which are supported on the hydraulic cylinder (203) and act against one another.
10. Torsional vibration damper according to Claim 9, characterised in that the springs (225) are weaker than the spring elements (221) and are supported through the latter on the hydraulic cylinder (203).
11. Torsional vibratior damper according to Claim 8 or 9, characterised in that the springs are formed as corrugated springs (225).
12. Torsional vibration damper according to ode of Claims 1 to 11, characterised in that the damper elementa are arranged by pairs in the windows (25, 29), while the pistons (307, 309) of each pair have a common piston rod (311) and the hydraulic cylinders (303, 305) are axially movable in relation to one another, and in that a further spring element (323) is arranged axially between the hydraulic cylinders (303, 305), through which the hydraulic cylinders (303, 305) are resiliently supported against one another.
13. Torsional vibration damper according to Claim 12, characterised in that the further spring element (323) is guided radially on the piston rod (311) and is held initially stressed between stop faces of a housing (325) which are directed axially towards one another.
14. Torsional vibration damper according to Claim 12 or 13 in combination with one of Claims 2 to 6, characterised in that the spring element (335, 337) arranged in the hydraulic cylinder (303, 305) is arranged on the side of the piston facing the other piston (307, 309) in each case.
15. Torsional vibration damper according to one of Claims 1 to 14, characterised in that the constricted passage (43; 111; 211; 317, 319) is provided between the circumference of the piston (37; 105; 207; 307, 309) and a cylinder wall (113) enclosing the piston.
16. Torsional vibration damper according to Claim 15, characterised in that the cylinder wall (113) enclosing the piston (105) is domed in barrel form.
17. A torsional vibration damper as claimed in claim 1, substantially as described herein with reference to and as illustrated by any one of the examples shown in the accompanying drawings.
GB08601543A 1985-01-23 1986-01-22 Torsional vibration damper Withdrawn GB2170882A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19853502029 DE3502029A1 (en) 1985-01-23 1985-01-23 TORSION DAMPER FOR CLUTCH DISCS WITH HYDRAULIC DAMPING

Publications (2)

Publication Number Publication Date
GB8601543D0 GB8601543D0 (en) 1986-02-26
GB2170882A true GB2170882A (en) 1986-08-13

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Family Applications (1)

Application Number Title Priority Date Filing Date
GB08601543A Withdrawn GB2170882A (en) 1985-01-23 1986-01-22 Torsional vibration damper

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DE (1) DE3502029A1 (en)
FR (1) FR2576381A1 (en)
GB (1) GB2170882A (en)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0339805A2 (en) * 1988-04-01 1989-11-02 Toyota Jidosha Kabushiki Kaisha Torsional damper type flywheel device with a damping mechanism utilizing a fluid flow
US5156067A (en) * 1988-04-01 1992-10-20 Toyota Jidosha Kabushiki Kaisha Torsional damper type flywheel device
US5269199A (en) * 1988-04-01 1993-12-14 Toyota Jidosha Kabushiki Kaisha Torional damper type flywheel device
EP1040918A1 (en) * 1999-03-31 2000-10-04 Heidelberger Druckmaschinen Aktiengesellschaft Method and device for damping the torsional vibrations of a printing machine
FR3023598A1 (en) * 2014-07-11 2016-01-15 Valeo Embrayages TORQUE TRANSMISSION DEVICE FOR A MOTOR VEHICLE
EP3043035A1 (en) * 2015-01-09 2016-07-13 Deere & Company A coupler for translating rotational forces

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4130089C2 (en) * 1991-09-11 1994-03-31 Ruecker Ges Mit Beschraenkter Friction disc clutch
DE19909914B4 (en) * 1999-03-06 2004-09-09 Mtu Friedrichshafen Gmbh Hydraulic damping element
DE10254725A1 (en) * 2002-11-23 2004-06-03 Adam Opel Ag Flywheel for reduction of rotational uniformity of drive shafts especially in motor vehicles has fluid containing chambers around the wheel

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0339805A2 (en) * 1988-04-01 1989-11-02 Toyota Jidosha Kabushiki Kaisha Torsional damper type flywheel device with a damping mechanism utilizing a fluid flow
EP0339805A3 (en) * 1988-04-01 1990-05-23 Toyota Jidosha Kabushiki Kaisha Torsional damper type flywheel device with a viscous damping mechanism
US5156067A (en) * 1988-04-01 1992-10-20 Toyota Jidosha Kabushiki Kaisha Torsional damper type flywheel device
US5269199A (en) * 1988-04-01 1993-12-14 Toyota Jidosha Kabushiki Kaisha Torional damper type flywheel device
EP1040918A1 (en) * 1999-03-31 2000-10-04 Heidelberger Druckmaschinen Aktiengesellschaft Method and device for damping the torsional vibrations of a printing machine
US6499401B1 (en) 1999-03-31 2002-12-31 Heidelberger Druckmaschinen Ag Method and device for absorbing torsional vibrations of a printing machine
FR3023598A1 (en) * 2014-07-11 2016-01-15 Valeo Embrayages TORQUE TRANSMISSION DEVICE FOR A MOTOR VEHICLE
EP3043035A1 (en) * 2015-01-09 2016-07-13 Deere & Company A coupler for translating rotational forces
US9664251B2 (en) 2015-01-09 2017-05-30 Deere & Company Coupler for translating rotational forces

Also Published As

Publication number Publication date
GB8601543D0 (en) 1986-02-26
FR2576381A1 (en) 1986-07-25
DE3502029A1 (en) 1986-07-31

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WAP Application withdrawn, taken to be withdrawn or refused ** after publication under section 16(1)