WO2014135144A1 - Amortisseur de vibrations de torsion présentant au moins un côté primaire et un côté secondaire - Google Patents

Amortisseur de vibrations de torsion présentant au moins un côté primaire et un côté secondaire Download PDF

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Publication number
WO2014135144A1
WO2014135144A1 PCT/DE2014/000091 DE2014000091W WO2014135144A1 WO 2014135144 A1 WO2014135144 A1 WO 2014135144A1 DE 2014000091 W DE2014000091 W DE 2014000091W WO 2014135144 A1 WO2014135144 A1 WO 2014135144A1
Authority
WO
WIPO (PCT)
Prior art keywords
helical spring
coil spring
spring
torsional vibration
vibration damper
Prior art date
Application number
PCT/DE2014/000091
Other languages
German (de)
English (en)
Inventor
Ulrich Rohs
Original Assignee
Ulrich Rohs
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 Ulrich Rohs filed Critical Ulrich Rohs
Priority to CN201480012511.3A priority Critical patent/CN105008760B/zh
Priority to DE112014001176.2T priority patent/DE112014001176A5/de
Publication of WO2014135144A1 publication Critical patent/WO2014135144A1/fr

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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
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/1232—Wound springs characterised by the spring mounting
    • F16F15/12326—End-caps for 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
    • 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
    • F16F15/134—Wound springs
    • F16F15/1343—Wound springs characterised by the spring mounting
    • F16F15/13438—End-caps for springs

Definitions

  • the invention relates to a torsional vibration damper with at least one primary side and a secondary side, which are rotatably supported against each other, and with an effective between the primary side and the secondary side spring-damper device which comprises at least a two-sided coil spring which between at least a first contact with a first of its sides and at least one second contact with the second of its sides is resiliently effective and is positioned on both sides via helical spring positions.
  • Such a torsional vibration damper is described for example in International Patent Application WO 2005/100817 AI as a two-mass flywheel with a primary mass, a spring system and a secondary mass.
  • individual springs between carriers of mutually movable components of the two-mass flywheel are arranged.
  • the drivers are components of flyer rings, which are mutually movably arranged between the primary mass and the secondary mass and provide mutually movable components of the two-mass flywheel.
  • the provided springs reduce in interaction with the mentioned mutually movable components vibrations between the primary mass and the secondary mass.
  • the inserted springs are positioned by means of helical spring positioning relative to the primary mass and the secondary mass.
  • the helical spring positions comprise helical spring shoes, wherein
  • each screw spring end a helical spring shoe, a coil spring positioning and a system against which presses the coil spring shoe, which each comprise one of the two coil spring positions and which are arranged on a common assembly provided.
  • the object of the invention is a torsional vibration damper with at least one primary side and a secondary side, which are rotatably supported against each other, and with an effective between the primary side and the secondary side spring-damper device which comprises at least a two-sided coil spring, which is resiliently effective between at least one first abutment with a first one of its sides and at least one second abutment with the second of its sides and which is positioned on both sides via helical spring positions, wherein a first of the two helical spring positions in the circumferential direction is achieved by means of a support structure bridging the helical spring Freely supporting is provided on the first coil spring positioning opposite plant is positioned.
  • a further developed embodiment provides in this context that the first of the two helical spring positioning is arranged at a free end of a helical spring preferably substantially cross-arm as a support structure.
  • a possibility is created that a coil spring is reliably guided in the smallest space on a coil spring positioning.
  • a special Platzerspamis in the construction of torsional vibration dampers in particular with regard to the storage of the axial ends of inserted coil springs, namely achieved when the coil spring bridging support structure is housed within the coil spring, so that the space volume of a provided on a torsional vibration damper spring is optimally used.
  • a further advantageous embodiment provides that the arm carries or has the second of the two helical spring positions, preferably at its end opposite its free end. This ensures by means of simple measures that the coil springs on both sides are held securely on only one coil spring positioning and thus an optional support of the coil springs is achieved.
  • a preferred embodiment variant is characterized in that the first of the two helical spring positions on the side of the respective helical spring is radially outwardly supported on at least one inner turn of the helical spring and the second of the two helical spring positions radially inward on at least one inner turn the helical spring supported.
  • the coil spring bridging support assembly of the first of the two coil spring positions can be formed by the coil spring and the second of the two coil spring positions. Due to the arrangement of a coil spring positions outside and the other inside, the coil spring nachwievor, although it is part of the support assembly, be freely compressed and yet be supported against centrifugal force to the outside.
  • the first of the two coil spring positions on the side of the respective coil spring is radially inwardly supported on at least one inner turn of the coil spring and the second of the two coil spring positions radially outward at least one inner Winding the coil spring is supported, so that the helical spring bridging support assembly of the first of the two coil spring positions is formed by the coil spring and the second of the two coil spring positions.
  • internal winding refers to a turn of the respective coil spring, which is not found at the end of the respective coil spring and can come in shock with any equipment, aviators or the like in contact.
  • At least one turn that supports the first coil spring position is not located farther from the opposite side of the coil spring than the first coil spring position, at least one turn supported by the second coil spring position is structurally secured by simple means; in that at least one turn is supported both by the second helical spring positioning and also supports the first helical spring positioning. This leads to a very stable design of the entire support structure.
  • a Coil spring shoe includes. Such a helical spring shoe can be easily replaced after signs of wear, without having to make a replacement with regard to the existing coil spring positions. In particular, such a helical spring shoe can optionally also be made correspondingly more stable from the outset than, for example, a system or even a helical spring.
  • the circumference of a helical spring or a peripheral area around a helical spring is as small as possible when the helical spring shoe bears against the helical spring from the inside.
  • the helical spring shoe can act in a structurally particularly simple manner between a coil spring positioning and a coil spring. Cumulatively or alternatively, it is advantageous if the helical spring shoe bears against the outside of the coil spring. In this way, an advantageous contact between a coil spring and, for example, a primary or secondary side of a torsional vibration damper can be achieved.
  • a helical spring shoe can on the one hand act particularly well between a screw positioning and a helical spring and, on the other hand, advantageously form a contact surface between a helical spring and an arm extending through the helical spring, when the helical spring shoe is arranged at a free end of an arm which essentially crosses through the helical spring as a carrying arrangement , If the helical spring shoe is provided, for example, as a supplement to the support arrangement for a helical spring, the helical spring is mounted particularly well on a helical spring positioning.
  • a helical spring can be subjected to a particularly uniform load when the helical spring is designed to be straight.
  • a rectilinear coil spring can deliver their spring or damper properties to components of the torsional vibration damper particularly evenly.
  • the torsional vibration damper as a whole also has an improved response behavior.
  • the rectilinear coil springs can also be connected in series, for example by aviators, which may possibly also be arranged on flyer rings, in order to be able to simulate longer springs.
  • curved springs can be simulated, which are not so advantageous in accordance with the above-mentioned properties of linear springs and otherwise also more expensive.
  • the object of the present invention is also a torsional vibration damper, in particular also formed with one of the features explained above, with at least one primary side and a secondary side, which are rotatably mounted against each other, and with a between the primary side and the secondary side effective spring-damper device comprising at least a two-sided coil spring which is resiliently effective between a first contact with a first of its sides and a second contact with the second of its sides and which is positioned on both sides via helical spring positions, wherein the torsional vibration is characterized in that both coil spring positions on a common flyer, which is preferably arranged on an airman ring, in particular together with other flyers, are positioned.
  • this makes it possible to completely hold a helical spring with regard to its two ends to helical spring positions of a single flyer.
  • it is possible to dispense with helical spring positioning on the primary and / or secondary side which, in addition, may even have to be alternately held in a holding manner.
  • This in turn has a particularly positive effect on a further reduction in space.
  • a possible noise emission is greatly reduced.
  • FIG. 1 shows schematically a cross section of a torsional vibration damper with coil spring positioning, which partially comprise a helical spring bridging and curved support structure
  • FIG. 2 is a schematic view of a detailed view of helical spring positions, each with a support arrangement bridging a helical spring;
  • FIG. 3 schematically shows a further detail view of the torsional vibration damper
  • Coil spring positioning partially comprising a coil spring bridged alternative shaped support structure
  • Figure 4 schematically shows a further detail view of the torsional vibration damper
  • Coil spring positioners which partially comprise a less curved support structure bridging a coil spring
  • Figure 5 schematically shows a further detail view of the torsional vibration damper
  • Coil spring positioning which partially comprise a helical spring bridging barely curved configured support assembly
  • Figure 6 schematically and exemplarily a longitudinal section of a torsional vibration damper with three mutually acting flyer rings
  • Figure 7 schematically shows a cross section of an alternative torsional vibration damper with a helical spring positioning with externally and internally disposed on the coil spring helical spring shoes.
  • the torsional vibration damper 1 shown in FIG. 1 and FIG. 2 (detail view) has a primary side 2 and a secondary side 3, which are rotatably mounted to one another. Between the primary side 2 and the secondary side 3, a spring-damper device 4 is arranged, by means of which vibrations of the torsional vibration damper 1 can be damped.
  • the spring-damper device 4 consists in this case of a first spring-damper unit 5, a second spring-damper unit 6 and a third spring-damper unit 7, wherein the spring-damper units 5, 6 and 7 are arranged one behind the other concentrically about a central flange 8 of the torsional vibration damper 1. All spring-damper units 5, 6 and 7 are identical. Each of the spring-damper units 5, 6 and 7 is arranged in a designated helical spring receiving space 9, 10 and 11 of the torsional vibration damper 1.
  • the first coil spring receiving space 9 extends between a first primary side elevation 12 and a second primary side elevation 13. Accordingly, the second coil spring receiving space 10 extends between the second primary side elevation 13 and a third primary side elevation 14 and the third coil spring accommodating space 11 between the third primary side elevation 14 and the first primary page elevation 12th
  • Each of the three spring-damper units 5, 6, 7 in this embodiment comprises a first coil spring 15, a second coil spring 16, a third coil spring 17 and a fourth coil spring 18, the first coil spring 15 and the fourth coil spring 18 and the second coil spring 16 and the third coil spring 17 are each formed identically.
  • the coil springs 15, 16, 17 and 18 are numbered only with regard to the first coil spring receiving space 9.
  • a first aviator 19 of a first aviator ring 20, a second aviator 21 of a second aviator ring 22 and a third aviator 23 of a third aviator ring (not shown here) placed.
  • All flyer rings that is to say the first flyer ring 20, the second flyer ring 22 and the third flyer ring not shown in this figure (but see FIG. 6, reference number 55), are arranged so as to be rotationally concentric with one another about the central flange 8.
  • the first aviator 1 forms a first coil spring position 24, a second coil spring position 25, and a third coil spring position 26.
  • the rovenfederderleiteren 24, 25 and 26 are designed differently.
  • the second flyer 21 essentially forms two identical helical spring positions 27 (fourth helical spring positioning) and 28 (fifth helical spring positioning), whereas the third flyer 23 again forms three non-identical helical spring positioning positions.
  • gene namely, a sixth coil spring positioning 29, a seventh coil spring positioning 30 and an eighth coil spring positioning 31st
  • the first helical spring positioning 24 of the first flyer 19 is realized in a particularly space-saving manner by means of a carrying arrangement 32 bridging the helical spring 15 on the first flyer 19.
  • the bridging support assembly 32 connects the first coil spring positioning 24 directly to the second coil spring positioning 25, wherein the bridging support assembly 32 may be considered as an extension of the second coil spring positioning 25 of the first flyer 19.
  • the bridging support assembly 32 extends within the coil spring 15, whereby a first end 33 of the coil spring 15 is on the one hand reliable and on the other in a particularly space-saving manner to primary or secondary systems 34 and / or 35 is positioned the first coil spring 24 directly opposite.
  • the first or primary-side system 34 is the primary side 2 of the torsional vibration damper 1 and the second or secondary-side system 35 is the secondary side 3 of the torsional vibration damper 1 associated.
  • another end 37 of the coil spring 15 is reliably positioned by means of the second helical spring positioning 25 of the first flyer 19.
  • the helical spring positioning 25 as a bridging carrying arrangement 32 has an arm 38 which essentially passes through the helical spring 15 substantially.
  • the aviator 23 is constructed.
  • the sweeping arm 38 is curved toward the central flange 8 in this exemplary embodiment, so that a recess 39 is formed on the underside.
  • a compression of the coil spring 15 when the spring forces press the corresponding turn against the corresponding system 34, 35 and 36 and the coil spring 15 is positioned in this way, an undesired rubbing of the coil spring 1 can be avoided.
  • an approximately resulting coil spring belly or the center of the helical spring 15 is sufficiently prevented from migrating radially.
  • helical spring shoes 40 (for the sake of clarity overall only once) are numbered at the helical spring positions 25, 26, 27, 28, 29 and 30 ) intended.
  • the coil springs 15, 16, 17 and 18, in particular with the helical spring positions 25, 26, 27, 28, 29 and 30 cooperate significantly better, since by means of these helical spring shoes 40 more turns of the coil springs 15, 16, 17 and 18th can be achieved.
  • the helical spring shoes 40 are preferably loosely or movably attached to the respective helical spring ments 25, 26, 27, 28, 29 and 30 are mounted, the mobility of the individual ringenfe- 15, 16, 17 and 18 relative to the ringenfederpositionierungen 25, 26, 27, 28, 29 and 30 is not or only slightly limited.
  • the helical spring positions 24 and 31 provided by means of the bridging support assemblies 32 are dispensed with such helical spring shoes 40, also because the respective cross arm 38 of the bridging support assemblies 32 extends along the helical springs 15 and 18.
  • the flyer 19 from the first screw spring receiving space 9 on the primary side elevation 12 faces an identically constructed further flyer 23 "in the third helical spring receiving space 11.
  • the fliers 19 and 23 and fliers of identical design which with '(second coil spring receiving space 10) and which are marked with' (third coil spring receiving space 1 1), and on the other hand, the spring-damper units 5, 6 and 7 are identical, will be omitted a further explanation of such marked components also to avoid such repetitions.
  • the torsional vibration damper 1 has an alternative first flyer 19A and correspondingly an alternative further flyer 23 "A, which are opposite to the first flyer 19 and third flyer described above 23 is characterized by alternatively configured coil spring positioning 24A (numbered only with respect to the flyer 19A.)
  • the coil spring positioning 24A is less curved toward the center flange 8 than the coil spring positioning 24 previously described.
  • the helical spring positioning 24A configured in this way provides the first end 33 of the helical spring 15 with particularly good hold within the helical spring receiving space 9, so that the helical spring 15 is safely placed in front of the plants 34 and 35.
  • the helical spring position 24A of the detailed view 51 shown in FIG. 3 different from the helical spring position 24 of the torsional vibration damper 1 described in FIGS. 1 and 2, but also an arm 38A of a bridging support arrangement 32A passing through in this respect.
  • the sweeping arm 38A is designed to be less long.
  • FIG. 4 Another alternative first flyer 19B is illustrated in a detail view 52 of FIG. 4, with the alternative flyer 19B being characterized by a still more extended helical spring positioning 24B and by a straight elongate, through-going arm 38B. Accordingly, a related thereto the coil spring 15 bridging support structure 32B with its the coil spring 15 cross-arm 38B is alternatively formed.
  • the coil spring 15 within the coil spring receiving space 9 may indeed move further outward, since a no longer so strong recess 39B is provided.
  • the coil spring positioning 24B and the penetrating arm 38B still provide sufficient guidance so that critical formation of a coil spring crimp can be counteracted to a sufficient extent.
  • a formation of such a coil spring belly can likewise be counteracted by means of a helical spring positioning 24C (FIG. 5) shown in a further detailed view 53, although in a region of a penetrating arm 38C a recess 39C is even less pronounced than the recess 39B of the sweeping arm 38B of the embodiment of FIG. 4.
  • the helical spring positioning 24C is also arranged on a flyer 19C by means of a support arrangement 32C passing through the helical spring 15, so that the primary-side abutment 34 and the secondary-side abutment 35 themselves need not be equipped with a helical spring positioning.
  • the torsional vibration damper 1 can be built as compact as in the previous embodiments of the detail views 50, 51 and 52 of Figures 2, 3 and 4.
  • a further view of the torsional vibration damper 1 is shown in FIG. Clearly visible here is how the first flyer ring 20, the second flyer ring 22 and the third flyer ring 55 are arranged axially one behind the other in the torsional vibration damper 1.
  • the primary side 2 and the secondary side 3 in conjunction with the central flange 8 are also easy to recognize. In the region of the sweeping arm 38, the first coil spring 15 can be seen.
  • FIG. 7 shows an exemplary embodiment of a further torsional vibration damper 60 which has a toothed rim 62 on a primary side 61 on the outside.
  • the torsional vibration damper 60 has a secondary side 63.
  • the primary side 61 and the secondary side 63 are rotatable relative to each other and form helical spring receiving spaces 64 and 65.
  • a first flyer 66 and a second flyer 67 are disposed within the two coil spring receiving spaces 64, 65.
  • the first flyer 66 is operatively connected via a first helical spring inner shoe 68 to a first helical spring 70 and via a second helical spring inner shoe 69 to a second helical spring 71.
  • At least the second coil spring 71 has a coil spring outer shoe 72, which is arranged between the second coil spring 71 and the primary side 61 and the secondary side 63 of the torsional vibration damper 60.
  • a further helical spring inner shoe 74 is provided between a further helical spring 73 and the second aviator 67, and an additional helical spring outer shoe 75 is provided between the helical spring 73 and the primary side 61 and the secondary side 63.
  • a further helical spring 76 is attached by means of a helical spring inner shoe 77 stored the second aviator 67.
  • the coil springs 70, 71, 73 and 76 are advantageously in communication with the two wings 66 and 67, respectively, when the helical spring shoes are made of a hard wear-resistant material.
  • forces can advantageously be transferred because of the good support options.
  • the helical spring inner shoes 69 and 74 protrude, as can be seen in FIG. 7, into the respective springs 71 and 73 so far that the two helical spring outer shoes 72, 75 overlap the respective helical spring inner shoes 69, 74, so that at least one turn of the Coil springs 71, 73 as part of a support assembly the respective fferenfedernau- .schuh 72, 75 wear, which in turn serves as a coil spring positioning.
  • the fliers 66, 67 are each arranged on flyer rings.

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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)
  • Springs (AREA)
  • Vibration Prevention Devices (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention vise à perfectionner un amortisseur de vibrations de torsion. A cet effet, l'amortisseur de vibrations de torsion selon l'invention présente au moins un côté primaire et un côté secondaire, disposés de manière à pouvoir tourner l'un contre l'autre, et un dispositif amortisseur à ressort agissant entre le côté primaire et le côté secondaire et comprenant au moins un ressort hélicoïdal à deux faces qui amortit avec une première de ses faces contre au moins un premier plan et avec sa deuxième face contre un second plan et qui est positionné sur ses deux faces en des emplacements de ressort hélicoïdal, un premier des deux emplacements de ressort hélicoïdal, dans le sens périphérique, étant placé sur un plan opposé au premier emplacement de ressort hélicoïdal, au moyen d'un dispositif support pontant le ressort hélicoïdal.
PCT/DE2014/000091 2013-03-05 2014-03-05 Amortisseur de vibrations de torsion présentant au moins un côté primaire et un côté secondaire WO2014135144A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201480012511.3A CN105008760B (zh) 2013-03-05 2014-03-05 具有至少一个主动侧和一个从动侧的扭转减振器
DE112014001176.2T DE112014001176A5 (de) 2013-03-05 2014-03-05 Torsionsschwingungsdämpfer mit zumindest einer Primärseite und einer Sekundärseite

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013003627.5A DE102013003627A1 (de) 2013-03-05 2013-03-05 Torsionsschwingungsdämpfer mit zumindest einer Primärseite und einer Sekundärseite
DE102013003627.5 2013-03-05

Publications (1)

Publication Number Publication Date
WO2014135144A1 true WO2014135144A1 (fr) 2014-09-12

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PCT/DE2014/000091 WO2014135144A1 (fr) 2013-03-05 2014-03-05 Amortisseur de vibrations de torsion présentant au moins un côté primaire et un côté secondaire

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CN (1) CN105008760B (fr)
DE (2) DE102013003627A1 (fr)
WO (1) WO2014135144A1 (fr)

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WO2019192645A1 (fr) * 2018-04-05 2019-10-10 Schaeffler Technologies AG & Co. KG Poulie d'embrayage à amortisseur à bascule pendulaire comportant un équipement de friction ; et embrayage à friction

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CN107304794B (zh) * 2016-04-18 2020-07-24 北汽福田汽车股份有限公司 车辆及其扭转减振器
DE102017204146A1 (de) 2017-03-14 2018-09-20 Bayerische Motoren Werke Aktiengesellschaft Torsionsschwingungsdämpfer sowie Antriebsstrang für ein Fahrzeug
US10520040B2 (en) * 2017-11-21 2019-12-31 Schaeffler Technologies AG & Co. KG Spring retainer for arc spring of a clutch
CN110259187B (zh) * 2019-07-17 2021-10-22 西南石油大学 一种用于矫正支撑的支撑点定位底座
CN113623361A (zh) * 2021-08-17 2021-11-09 哈尔滨工业大学 基于预拉伸弹簧的扭转负刚度隔振装置

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WO2005100817A1 (fr) 2004-04-07 2005-10-27 Rohs-Voigt Patentverwertungsge- Sellschaft Mbh Volant a deux masses, comportant une masse primaire, un systeme de ressort et une masse secondaire
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DE102008063015A1 (de) 2008-12-23 2010-07-01 GAT Gesellschaft für Antriebstechnik mbH Torsionsschwingungsdämpfer mit einer Primärseite und Verfahren zum Herstellen einer Primärmasse eines Torsionsschwingungsdämpfers
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FR2371609A1 (fr) * 1976-11-17 1978-06-16 Ferodo Sa Dispositif amortisseur de torsion notamment pour friction d'embrayage, en particulier de vehicule automobile
EP0216476A1 (fr) * 1985-08-26 1987-04-01 Borg-Warner Automotive, Inc. Plateau mené d'embrayage avec répartition du décalage de friction
DE4201370C1 (en) 1992-01-20 1993-02-11 Hurth Getriebe Und Zahnraeder Gmbh, 8000 Muenchen, De Resilient spring drive for ic engine - connects drive input and output members using coil springs separated by spacers on curved rod
DE19751029A1 (de) * 1996-11-21 1998-05-28 Valeo Zweimassen-Dämpfungsschwungrad für Kraftfahrzeuge
DE19810500A1 (de) 1997-03-27 1998-10-01 Mannesmann Sachs Ag Torsionsschwingungsdämpfer mit einer Dämpfungseinrichtung
DE19729669A1 (de) 1997-07-11 1999-01-14 Rohs Voigt Patentverwertungsge Torsionsschwingungsdämpfer mit mindestens einer an einer Scheibe tangential angeordneten Feder
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DE112014001176A5 (de) 2015-11-12
CN105008760B (zh) 2018-08-31
DE102013003627A1 (de) 2014-09-11

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