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WO1999041525A1 - Systeme amortisseur - Google Patents

Systeme amortisseur Download PDF

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Publication number
WO1999041525A1
WO1999041525A1 PCT/GB1999/000454 GB9900454W WO9941525A1 WO 1999041525 A1 WO1999041525 A1 WO 1999041525A1 GB 9900454 W GB9900454 W GB 9900454W WO 9941525 A1 WO9941525 A1 WO 9941525A1
Authority
WO
WIPO (PCT)
Prior art keywords
damping device
spring
linkage
parts
pivot
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.)
Ceased
Application number
PCT/GB1999/000454
Other languages
English (en)
Inventor
Alastair John Young
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.)
Automotive Products PLC
Original Assignee
Automotive Products PLC
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 Automotive Products PLC filed Critical Automotive Products PLC
Priority to JP54121699A priority Critical patent/JP2001520737A/ja
Priority to EP99932520A priority patent/EP0986711A1/fr
Priority to AU44812/99A priority patent/AU4481299A/en
Priority to GB9923478A priority patent/GB2338773B/en
Publication of WO1999041525A1 publication Critical patent/WO1999041525A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F16F15/1204—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 with a kinematic mechanism or gear system
    • 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
    • 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
    • F16F15/131—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 rotating system comprising two or more gyratory masses
    • F16F15/133—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 rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/1333—Spiral springs, e.g. lying in one plane, around axis of rotation
    • 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
    • F16F2236/00—Mode of stressing of basic spring or damper elements or devices incorporating such elements
    • F16F2236/08—Torsion
    • 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
    • F16F2236/00—Mode of stressing of basic spring or damper elements or devices incorporating such elements
    • F16F2236/12—Mode of stressing of basic spring or damper elements or devices incorporating such elements loaded in combined stresses
    • 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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type

Definitions

  • the present invention relates to damping devices which include at least one spring to damp and/or
  • damping devices can be used in vehicle transmissions as part of a twin mass flywheel or in a fluid coupling
  • the spring is acted upon in one particular manner for example the spring 55 of DE3721710 is only axially compressed along its curved axis and the
  • spring 17 of FR2518203 is only put into tension by extending the spring along its axis as the input
  • the device including co-axially arranged first and second parts which can rotate relative to each other by a limited amount in response to torsional vibrations and/or torque fluctuations in the drive
  • said first and second parts forming, in use, part of a torque transmission path of the drive line
  • the device also including a spring which is stressed in at least two independent manners to resist
  • the spring is also stressed in a third independent manner to resist relative rotation of the first and second parts.
  • the spring may be a coil spring and one of the manners of stressing the spring may be by rotating a
  • one of the manners of stressing may be by applying a force to at
  • At least one coil in a radial direction with regard to the axis of the coil.
  • stressing the spring may be by applying a force substantially perpendicular to the arm
  • a damping device for use in a drive line, the device including co-axially arranged first and second parts which can rotate relative to each
  • the device being interconnected by at least one linkage means, the device
  • a fiiction damper which acts directly on components pivotally connected by a pivot of the linkage means to resist relative rotation of the first and second parts and hence damp
  • the fiiction damper is arranged co-axially with the pivot of the linkage means.
  • damping device for use in a drive
  • the device including co-axially arranged first and second parts which can rotate relative to each
  • the damping device also including at least one linkage
  • the linkage device including a link pivotally connected by a pin with the first or
  • FIG.1 is an axial cutaway view taken along the line AA of FIG.2 of a damping device
  • FIG.2 is a radial view taken along the line BB of FIG.1;
  • FIG.3 is a radial view taken along the line CC of FIG.1;
  • FIG.4 is a developed view taken along the line EE of FIG.1;
  • FIG.5 is a view similar to FIG.1 with the damping device shown in a drive position;
  • FIG 6 is a view similar to FIG 1 with the damping device shown in an over-run position,
  • FIG 7 is an axial cut away view taken along the line FF of FIG 8 of a second embodiment
  • FIG 8 is a radial view taken along the line GG of FIG 7,
  • FIG 9 is a radial view taken along the line HH of FIG 7,
  • FIG 10 is a developed view taken along the line LI of FIG 1,
  • FIG 11 is an axial cut away view taken along the line JJ of FIG 12 of a third embodiment of
  • FIG 12 is a radial view taken along the line KK of FIG 11, and
  • FIG 13 is an axial cutaway view similar to Fig 5 of a fourth embodiment of a damping
  • twin mass flywheel 1 incorporating a damping
  • the damping device includes first part 11 and a second part 12 which can rotate relative to each other via bearing 13
  • First part 11 consists of input plate 20 which is secured rotationally fast with and spaced from a
  • Second part 12 consists of output plate 30 and pivot plate 31 secured rotationally fast to the output
  • the damping device further consists of a plurality of linkage devices 40 and a plurality of springs 50
  • Each linkage device 40 comprises an anchor link 43 pivotally connected via a first pivot 44 to the
  • the linkage device 40 also includes a linkage
  • anchor link 43 is in the form of a pair of plates 43 A, 43B mounted one on each axial side of the link 41A (see FIG 2)
  • the spring 50 is generally in the form of a clock spring, that is to say a spring in which successive
  • coils are of a reduced radius thus enabling each successive coil to be mounted radially inside its
  • End 52 is in the form of a hook
  • Anchor link plates 43 A and 43B are mirror images of each other and each consist of a disk portion
  • a fiiction damping device 60 which is arranged co-axially of the first
  • the friction damping device 60 consists of a belleville spring 61 which acts on input plate 20 to bias a friction plate 62 towards link plate 43B The belleville spring load is reacted via link
  • the damping device 10 is installed in twin mass flywheel 1 which includes the additional
  • twin mass flywheel 1 rotates in a clockwise direction in the view shown in FIG 1 as indicated by arrow R Relative rotation between the input
  • each linkage device 40 and its associated spring 50 and fiiction device 60 is the same.
  • flywheel torsional stiflhess is relatively low.
  • FIG.1) and the link 41 A folds between the anchor plates 43 A, 43B.
  • controlling influence of the linkage arrangement is operable at any rotational speed of the flywheel 1 and also at any relative rotational position of the input and output plates.
  • anchor link 43 only rotates anti-clockwise as shown in FIG.1 from its neutral position
  • the spring 50 directly acts to resist pivotal movement of the first pivot by directly acting on the two
  • the spring 50 also, therefore, has the effect of resisting rotation of the input and output plates.
  • end of the spring and third manner is to apply a force to the coils in a radial direction with regard to
  • Friction plate 62 is rotationally fast with input plate 20 since tabs 62 A of the plate 62 engage holes
  • fiiction plate 63 or between fiiction plate 63 and cover plate 21 depending upon the relative
  • FIGS 7-10 show a second embodiment of a twin mass flywheel 101 inco ⁇ orating a damping
  • twin mass flywheel 110 which perform the same fimction as components of the twin mass
  • Third pivot 142 comprises a pin 146 rotationally fast with link 141 A (in this case via an interference
  • the pin projects on either lateral side of link 141 A when viewing FIG 8 and the ends of the pins act as bearings and can rotate relative to bushes 147 A and 147B which are secured by an
  • twin mass flywheel increasing the overall axial length of twin mass flywheel.
  • Spring 150 is constructed from wire with a round cross-section and consists of a pair of adjacent coils 154A and 154B connected via a bridging portion 155 near the centre of the coils.
  • Each arm 156 has an arm 156 projecting substantially tangentially from the coils 154A and 154B.
  • Each arm 156 has an arm 156 projecting substantially tangentially from the coils 154A and 154B.
  • Anchor link 143 is in the form of a pair of mirror image links 143 A, 143B. However each anchor link 143A, 143B has a notch 143H which in combination with bridging portion 155 of spring 150
  • springs could be used each having an end portion for engagement with the anchor link 143.
  • Rivet 143G acts in a cantilever fashion on arm 156B
  • Friction damping device 160 is arranged co-axially of the pivot 144.
  • fiiction plate 162 are identical to their counte ⁇ arts in twin mass flywheel 1. However fiiction plate 162 is identical to their counte ⁇ arts in twin mass flywheel 1. However fiiction plate 162 is identical to their counte ⁇ arts in twin mass flywheel 1. However fiiction plate 162 is identical to their counte ⁇ arts in twin mass flywheel 1. However fiiction plate 162 is identical to their counte ⁇ arts in twin mass flywheel 1. However fiiction plate 162 are identical to their counte ⁇ arts in twin mass flywheel 1. However fiiction plate
  • Second and third fiiction plates 164 and 166 are secured rotationally fast to anchor link 143 via bush 165.
  • FIGS.11 and 12 show a third embodiment of a damping device 210 installed in a fluid flywheel
  • the fluid flywheel is a torque converter though in further embodiments it could be a Fottinger coupling. 13
  • torque from the engine crankshaft 270 is transmitted via flex plate 271, housing 272, input impeller 273, hydraulic fluid 274, output impeller 275, and hub 275A to the gear box (not
  • cover plate 221 (in the form of a single annular plate) through the damping device 210, output plate
  • fiiction device there is no fiiction device but other embodiments may include a fiiction device.
  • the invention could equally be applied to dampers having any other suitable form of spring such as a helical or leaf spring for example.
  • Figure 13 shows a further embodiment twin mass flywheel inco ⁇ orating a damping device
  • the damping device comprises
  • an anchor link 343 pivotally connected via a first pivot 344 to a first part 311 and having a 14
  • the torque transmitting connection 341 comprises a generally circumferentially extending linkage 360 pivotally connected to the anchor link 343 via a second pivot 345 and two circumferentially spaced main links 341 A pivotally connected via third pivots 342 to the second part.
  • the main links being interconnected by the circumferentially extending linkage 360 via fourth pivots 362.
  • One end of a helical compression spring 350 is contacted by a spring abutment portion 361 on one end of the circumferentially extending linkage 360.
  • the other end of the spring contacts an abutment 370 mounted to the first part 311.
  • the geometry of the device is such that relative rotational displacement in either direction between the first 311 and second 312 parts results in compression of the spring 350 between abutments 361 and 370.
  • the spring 350 is also stressed following clockwise (as viewed in Fig. 13) rotational displacement of the first part 311 relative to the second part 312, i.e. during drive conditions, by the coils being squeezed between abutment 333 on the second part 312 and abutment 324 on the first part 311.
  • the spring 350 may comprise a pair of springs one mounted inside the other.

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  • 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

L'invention concerne un système(10) amortisseur adapté à une transmission. Ce système (10) amortisseur comprend une première et une seconde partie (11, 12) disposées de manière coaxiale, ces deux parties peuvent tourner l'une par rapport à l'autre sur une distance limitée en réaction aux vibrations en torsion et/ou aux fluctuations du couple dans la transmission. L'amortisseur comprend en outre un ressort (50) qui est sollicité au moins de deux façons distinctes de manière à résister à la rotation relative de la première et de la seconde partie (11, 12) et à amortir ainsi les vibrations et/ou les fluctuations. l'amortisseur (10) peut faire partie d'un volant (1) à double masse ou d'un coupleur hydraulique tel qu'un convertisseur de couple ou un embrayage hydraulique Föttinger. L'invention concerne en outre un amortisseur (10) dans lequel les première et seconde parties (11, 12) sont connectées par une liaison mécanique. L'invention concerne également un amortisseur (60, voir figure 3) à friction qui agit directement sur des composants connectés de manière pivotante par un pivot de la liaison mécanique, cet amortisseur à friction étant coaxial au pivot.
PCT/GB1999/000454 1998-02-13 1999-02-12 Systeme amortisseur Ceased WO1999041525A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP54121699A JP2001520737A (ja) 1998-02-13 1999-02-12 減衰装置
EP99932520A EP0986711A1 (fr) 1998-02-13 1999-02-12 Systeme amortisseur
AU44812/99A AU4481299A (en) 1998-02-13 1999-02-12 A damping device
GB9923478A GB2338773B (en) 1998-02-13 1999-02-12 A damping device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB9803047.1 1998-02-13
GBGB9803047.1A GB9803047D0 (en) 1998-02-13 1998-02-13 A damping device

Publications (1)

Publication Number Publication Date
WO1999041525A1 true WO1999041525A1 (fr) 1999-08-19

Family

ID=10826916

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB1999/000454 Ceased WO1999041525A1 (fr) 1998-02-13 1999-02-12 Systeme amortisseur

Country Status (5)

Country Link
EP (1) EP0986711A1 (fr)
JP (1) JP2001520737A (fr)
AU (1) AU4481299A (fr)
GB (2) GB9803047D0 (fr)
WO (1) WO1999041525A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8210951B2 (en) 2007-09-10 2012-07-03 Magna Powertrain Ag & Co Kg Dual-mass flywheel
WO2014092308A1 (fr) * 2012-12-14 2014-06-19 한국파워트레인 주식회사 Convertisseur de couple pour véhicule
WO2017042440A1 (fr) * 2015-09-10 2017-03-16 Valeo Embrayages Ensemble de transmission de couple pour un véhicule automobile
WO2017055590A1 (fr) * 2015-10-02 2017-04-06 Valeo Embrayages Dispositif d'accouplement de couple hydrocinétique pour véhicule à moteur
WO2017055602A1 (fr) * 2015-10-02 2017-04-06 Valeo Embrayages Dispositif d'accouplement de couple hydrocinétique pour véhicule à moteur
DE102016011143A1 (de) 2016-09-15 2018-03-15 Borgwarner Inc. Drehschwingungstilger, Torsionsschwingungsdämpfer mit einem solchen Drehschwingungstilger und Antriebsstrang mit einem solchen Drehschwingungstilger
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

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191216584A (en) * 1912-07-16 1913-07-10 John James Raynes Apparatus for Equalising the Driving Power from Internal Combustion Engines.
FR2518203A1 (fr) 1981-12-11 1983-06-17 Peugeot Volant amortisseur de vibrations, notamment pour vehicule automobile
DE3721710A1 (de) 1986-07-05 1988-01-07 Luk Lamellen & Kupplungsbau Einrichtung zum daempfen von schwingungen
WO1992014076A1 (fr) * 1991-01-30 1992-08-20 Automotive Products Plc Volant-moteur a deux masses d'inertie
GB2284875A (en) * 1993-12-06 1995-06-21 R & D Marine Ltd Flexible coupling
WO1996006289A1 (fr) * 1994-08-20 1996-02-29 Automotive Products Plc Volant d'inertie a double masse
US5558317A (en) * 1994-01-26 1996-09-24 General Motors Corporation Volute springs adapted for torsional damper assemblies and method of manufacturing same
DE19538722A1 (de) * 1995-10-18 1997-04-24 Fichtel & Sachs Ag Torsionsschwingungsdämpfer mit Koppelelementen
DE19721236A1 (de) * 1996-05-28 1997-12-04 Luk Lamellen & Kupplungsbau Torsionsschwingungsdämpfer

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9603268D0 (en) * 1996-02-16 1996-04-17 Automotive Products Plc Twin Mass Flywheel

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191216584A (en) * 1912-07-16 1913-07-10 John James Raynes Apparatus for Equalising the Driving Power from Internal Combustion Engines.
FR2518203A1 (fr) 1981-12-11 1983-06-17 Peugeot Volant amortisseur de vibrations, notamment pour vehicule automobile
DE3721710A1 (de) 1986-07-05 1988-01-07 Luk Lamellen & Kupplungsbau Einrichtung zum daempfen von schwingungen
WO1992014076A1 (fr) * 1991-01-30 1992-08-20 Automotive Products Plc Volant-moteur a deux masses d'inertie
GB2284875A (en) * 1993-12-06 1995-06-21 R & D Marine Ltd Flexible coupling
US5558317A (en) * 1994-01-26 1996-09-24 General Motors Corporation Volute springs adapted for torsional damper assemblies and method of manufacturing same
WO1996006289A1 (fr) * 1994-08-20 1996-02-29 Automotive Products Plc Volant d'inertie a double masse
DE19538722A1 (de) * 1995-10-18 1997-04-24 Fichtel & Sachs Ag Torsionsschwingungsdämpfer mit Koppelelementen
DE19721236A1 (de) * 1996-05-28 1997-12-04 Luk Lamellen & Kupplungsbau Torsionsschwingungsdämpfer

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8210951B2 (en) 2007-09-10 2012-07-03 Magna Powertrain Ag & Co Kg Dual-mass flywheel
WO2014092308A1 (fr) * 2012-12-14 2014-06-19 한국파워트레인 주식회사 Convertisseur de couple pour véhicule
KR101431219B1 (ko) 2012-12-14 2014-08-18 한국파워트레인 주식회사 차량용 토크 컨버터
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
CN108350979A (zh) * 2015-09-10 2018-07-31 法雷奥离合器公司 用于机动车辆的扭矩传递组件
WO2017042440A1 (fr) * 2015-09-10 2017-03-16 Valeo Embrayages Ensemble de transmission de couple pour un véhicule automobile
US10753445B2 (en) 2015-09-10 2020-08-25 Valeo Embrayages Torque transmission assembly for a motor vehicle
US9822862B2 (en) 2015-10-02 2017-11-21 Valeo Embrayages Hydrokinetic torque coupling device for a motor vehicle
CN108351007A (zh) * 2015-10-02 2018-07-31 法雷奥离合器公司 用于机动车辆的液动扭矩联接装置
US9885406B2 (en) 2015-10-02 2018-02-06 Valeo Embrayages Hydrokinetic torque coupling device for a motor vehicle
WO2017055602A1 (fr) * 2015-10-02 2017-04-06 Valeo Embrayages Dispositif d'accouplement de couple hydrocinétique pour véhicule à moteur
WO2017055590A1 (fr) * 2015-10-02 2017-04-06 Valeo Embrayages Dispositif d'accouplement de couple hydrocinétique pour véhicule à moteur
CN108351007B (zh) * 2015-10-02 2021-12-03 法雷奥离合器公司 用于机动车辆的液动扭矩联接装置
DE102016011143A1 (de) 2016-09-15 2018-03-15 Borgwarner Inc. Drehschwingungstilger, Torsionsschwingungsdämpfer mit einem solchen Drehschwingungstilger und Antriebsstrang mit einem solchen Drehschwingungstilger

Also Published As

Publication number Publication date
GB9803047D0 (en) 1998-04-08
JP2001520737A (ja) 2001-10-30
GB2338773B (en) 2002-07-31
EP0986711A1 (fr) 2000-03-22
AU4481299A (en) 1999-08-30
GB9923478D0 (en) 1999-12-08
GB2338773A (en) 1999-12-29

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