EP3259490A1 - Torsional vibration damper - Google Patents
Torsional vibration damperInfo
- Publication number
- EP3259490A1 EP3259490A1 EP16708350.0A EP16708350A EP3259490A1 EP 3259490 A1 EP3259490 A1 EP 3259490A1 EP 16708350 A EP16708350 A EP 16708350A EP 3259490 A1 EP3259490 A1 EP 3259490A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- flange
- torsional vibration
- vibration damper
- input part
- stops
- 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- Withdrawn
Links
Classifications
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- 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
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- 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
- F16F15/1217—Motion-limiting means, e.g. means for locking the spring unit in pre-defined positions
Definitions
- the invention relates to a torsional vibration damper, in particular two-mass flywheel, comprising an input part and an output part with a common axis of rotation about which the input part and the output part rotatable together and are rotatable relative to each other limited, and effective between the input part and the output part spring damper Device having at least one energy store, and a secondary stop device, wherein the input part and the output part each have corresponding secondary stops.
- DE 195 22 718 A1 discloses a flange-like component is known for acting on at least two coil springs having force accumulators, which are arranged concentrically about the axis of rotation of the component, and between which ends to each other send ends is arranged in each case a radially extending arm of the component ,
- the arms - viewed in the axial direction - between support areas for the coil springs, z. B. on a housing, are arranged, wherein the arms can act both one of the ends facing each other with the coil springs, as well as the other, in which the arms for the one
- Applying direction at least one arm has a different from the / the other arm (s) differing shape in order to reduce a transition stiffness resulting from suspension and damping resistance in a transition to a thrust range to the lowest possible level and thereby a load on the springs also To keep low on a stress that results from the fact that the springs go to block.
- a torsional vibration damper is known from DE 10 2008 009 656 A1 with a drive-side and an output-side transmission element which are rotatable relative to one another at least one damping device provided therebetween with at least one circumferentially effective long helical spring, wherein the transmission elements act on loading areas for the screw drive. and radially within the coil spring at least a limitation of the rotation between the transmission elements effecting stop element is provided, wherein the stop element two to ten degrees before the maximum allowable compression of the coil spring is effective to the effective between the two transmission elements damping device, in particular the Energy storage formed by coil springs to protect against overloading.
- a torsional vibration damper in particular split flywheel, with a primary flywheel, which is rotatably connected to the drive shaft of an internal combustion engine, and with a secondary flywheel, against the resistance of at least two circumferentially effective energy storage devices in Pulling direction and in the thrust direction is rotatable relative to the primary flywheel having a primary impactor for the energy storage devices, wherein the primary impactor for the energy storage devices comprises an effective in the pulling direction
- Studentslastommes- device which is arranged together with the primary impactor in a common receiving space for the energy storage devices.
- the invention has for its object to improve a torsional vibration damper mentioned structurally and / or functionally.
- a failure of the energy storage should be avoided.
- a failure of a spring is to be avoided.
- driveability of a motor vehicle should be ensured in the event of a failure of the energy store.
- a stoppage of a motor vehicle should be prevented because of damage to the torsional vibration damper.
- an interruption of a drive train should be prevented.
- a favorable impact design of secondary attacks should be optimized.
- a burden should be reduced by impact forces.
- a torsional vibration damper in particular two-mass flywheel, comprising an input part and an output part with a common axis of rotation about which the input part and the output part rotatable together and rotatable relative to each other are limited, and effective between the input part and the output part
- Spring-damper device having at least one energy storage, and a secondary impactor, wherein the input part and the output part each have corresponding secondary stops, wherein the secondary stops of the input part and / or the secondary stops of the output part are formed by at least one additional flange.
- the secondary stops of the input part and / or the secondary stops of the output part are formed by at least one additional flange, the rigidity of the secondary stops in other areas can be structurally influenced, so that damage to components can be avoided or at least minimized in the event of overloading.
- the secondary stops of the output part can be formed by an additional flange.
- the secondary stops of the output part can be formed by a multi-part additional flange.
- the secondary stops of the output part can be formed by a two-part additional flange.
- the secondary stops of the input part can be formed by an additional flange.
- the secondary stops of the input part can be formed by a multi-part additional flange.
- the secondary stops of the input part can be formed by a two-part additional flange.
- the torsional vibration damper can be used for arrangement in a drive train of a motor vehicle.
- the drive train may include an internal combustion engine.
- the powertrain may include a friction clutch device.
- the friction clutch device may have a double clutch.
- the drive train may have a transmission.
- the transmission can be a dual-clutch transmission.
- the drive train may have at least one drivable wheel.
- the rotary damper can be used for the arrangement between the internal combustion engine and the friction clutch device.
- the torsional vibration damper may be part of the friction clutch device.
- the torsional vibration damper can NEN to reduce torsional vibrations, which are excited by periodic processes, especially in the internal combustion engine.
- the torsional vibration damper can be effective in the thrust direction and / or in the pulling direction.
- a thrust direction is a power flow direction directed toward the engine.
- a pulling direction is a power flow direction emanating from the internal combustion engine.
- the torsional vibration damper may be disposed in a pulley decoupler.
- a pulley decoupler reduces resonances, nonuniformities and dynamic forces in a belt drive.
- a pulley decoupler may be connected to a crankshaft on the input part side.
- a pulley decoupler can be connected output part with a pulley, which drives, for example, ancillaries.
- the input part and the output part can be mounted rotatable by means of a bearing.
- the input part can serve for the drive-side connection, in particular with the internal combustion engine.
- the output part can for
- input part and “output part” refer to a power flow direction emanating from the internal combustion engine.
- the at least one energy store can have at least one spring.
- the at least one spring may be a compression spring.
- the at least one spring may be a coil spring.
- the at least one spring may be a bow spring.
- the at least one energy store can be effective in the thrust direction and / or in the pulling direction.
- the at least one energy store can be effective with respect to the axis of rotation with an effective radius.
- the at least one energy store can be a high-capacity spring.
- a high-capacity spring is optimized for possible impacts. Impact is understood to mean an instantaneous impact load, as occurs, for example, in a dual-mass flywheel when the vehicle is stalled. Since it is difficult to completely avoid impacts, the impact must be reduced by increased bustiness of the torsional vibration damper. A high-capacity spring can make a significant contribution here.
- the at least one energy store may be a bow spring with an increased winding spacing.
- the at least one energy store can be a high-capacity bow spring.
- a high-capacity bow spring has an increased winding distance.
- the abutment torque of the bow spring can be substantially increased.
- a high capacity bow spring can save about 30% to 50% more energy compared to conventional bow springs without causing a stop.
- the wire thickness of a high-capacity bow spring can correspond approximately to the wire thickness of a conventional bow spring, so that the
- the nominal spring rate of a high capacity bow spring may be slightly higher than the nominal spring rate of a conventional bow spring.
- a high capacity bow spring helps to avoid deformation of the bow spring.
- the input part may have a flange portion.
- the input part can have a cover section.
- the flange portion and the lid portion can be firmly connected to each other, in particular welded, be.
- the flange portion and the lid portion may define a torus-like receiving space for the at least one first energy storage.
- the output part may have a flange part.
- the additional flange may be connected to the flange.
- the output part may have a flywheel part.
- the additional flange can be arranged axially between the flange part and the flywheel mass part.
- the flange, the additional flange and the flywheel part can be firmly connected.
- the flange part, the additional flange and the flywheel part can be riveted together.
- the flange portion of the output member may be disposed axially between the flange portion and the lid portion of the input member.
- the additional flange and the lid section can in be arranged the same axial position.
- the flywheel mass part can be arranged axially on a side of the cover section facing away from the flange section. The directions “axial” and “radial” are related to the axis of rotation.
- the flywheel mass portion of the output part may have a larger outer diameter than the effective radius of the at least one energy store.
- the spring-damper device may comprise a friction device.
- the input part may have primary stops.
- the flange portion may have primary stops.
- the lid portion may have primary stops.
- the primary attacks can protrude into the receiving space.
- the primary stops of the input part can serve to support the input part of the at least one energy store.
- the primary stops of the input section can be read using
- the primary stops of the input part can be arranged diametrically opposite one another.
- the flange part of the output part may have primary stops.
- the flange part of the output part can have radially outwardly projecting into the receiving space flange wings.
- the flange wings can form the primary stops of the output part.
- the primary stops of the output part can serve for the output part-side support of the at least one energy store.
- the primary stops of the output part can be arranged diametrically opposite one another.
- the at least one energy store can be supported on the one hand on the primary stops of the input part and on the other hand on the primary stops of the output part.
- the entrance part may have secondary impacts.
- the input part-side secondary strikes can be arranged on the cover section.
- the lid portion may have a recess into which project the input part-side secondary stops and are arranged in the output part side secondary strikes.
- the output part may have output partial secondary strikes.
- the output partial secondary strikes can be arranged on an additional flange.
- the input sub-side secondary attacks and the output sub-side secondary attacks can exceed a predetermined maximum Verwarwinkels between the input part and the output part come to mutual contact. Mutual concern of the input part secondary and the output part side secondary strikes can also be considered to be effective secondary strikes.
- the at least one energy store is preferably not yet loaded to block when reaching the maximum angle of rotation.
- the secondary stops of the input part and the secondary stops of the output part can come into contact with each other, without the energy storage is clamped to block. This minimizes or avoids damage to the energy storage.
- sliding shoes can be clipped onto the turns of the bow spring.
- the secondary stops can be arranged at a stop radius.
- the stop radius may be smaller than an effective radius of the at least one energy store.
- the secondary stops can each be diametrically opposed.
- the input part-side secondary attacks can each be diametrically opposed.
- the output sub-side secondary strikes can each be diametrically opposed.
- the input part-side secondary attacks can be arranged in the circumferential direction of the input part in each case centrally between the primary attacks.
- the input part-side secondary stops can be arranged in the circumferential direction of the input part in the middle in each case between the cover section-side primary stops.
- the output partial secondary strikes can be formed by an additional flange.
- the additional flange can consist of at least two flange segments. The flange segments may extend perpendicular to the axis of rotation.
- Flange segments can be made even.
- the flange segments can be flat sheets.
- the flange segments can be flat steel sheets.
- the additional flange can consist of exactly two flange segments.
- Two flange segments can be mirror-symmetrical.
- a flange segment may have a base body, a first stop wing and a second stop wing.
- a first main body of a flange segment may be formed curved around the axis of rotation of the torsional vibration damper.
- a flange segment can through holes have riveting with the output part.
- a flange segment may have through-holes in the base bodies for riveting with a flange part and a flywheel mass part of the starting part.
- the main body can have two end regions, in which it tapers in the radial direction and merges into a stop wing.
- a stop wing can be even.
- a stop wing may be a finger-shaped portion of a flange segment.
- a stop wing can extend approximately in the radial direction.
- a flange segment can have exactly two stop wings.
- An additional flange can have exactly two flange segments, each with exactly two flange wings.
- One of the two flange wings of a flange segment may be referred to as a first flange wing.
- Flange segment may be referred to as a second flange.
- the first flange wing and the second flange wing of a flange segment can be connected approximately diametrically opposite to a base body.
- the first flange wing and the second flange may be mirror-symmetrical.
- Two first stop wings of two flange segments of an additional flange may be arranged adjacent in the circumferential direction.
- Two first stop wings of two flange segments can form a secondary stop of the output part.
- Two second stop wings of two flange segments can be arranged adjacent in the circumferential direction.
- Two second stop wings of two flange segments can form a secondary stop of the output part.
- each of the two secondary stops is formed by two stop wings, the secondary stops each have a lower rigidity than a one-piece secondary stop of the same dimension.
- the secondary stops of the additional flange can thereby avoid or at least minimize damage to components in the drive train in an overload case.
- the ends of the stop wings may be remote from the axis of rotation.
- the stop wings can be arranged in the same plane as secondary stops of the input part. In the radial direction, the trajectories of the stop wings of the additional flange may overlap with the trajectories of secondary stops of the input part, so that a relative rotation between the input part and the output part is only possible to a limited extent.
- At least one of the secondary stops can be made so flexible that in an overload case damage to components, in particular in a drive train in which the torsional vibration damper is arranged, is avoided or minimized.
- the output part secondary strikes may have resilient stop wings.
- the flange segments of the additional flange may have resilient stop wings.
- the secondary stops can each have a voltage-optimized shape.
- the output partial secondary strikes may have a voltage-optimized shape.
- the invention relates to a dual mass flywheel with a split auxiliary flange in combination with a high-capacity spring.
- the invention includes a recess located in the primary-side cover with two or more stops.
- a two-part geometry and resilient flange of the additional flange should lead to the softest possible stop.
- the secondary side With a maximum twist, the secondary side can be turned relative to the primary side until the flange stops against the stops in the cover. Both components are so pronounced by appropriate design that even a certain residual rigidity of the system is permitted when being applied. This protects the remaining components in the drive train against overload.
- the invention can be used in dual mass flywheels and dampers as well as in
- Pulley decouplers are used. A failure of bow springs is avoided by a stop against overuse of the bow springs, in particular by a block state, protects. Preferably, high-capacity springs are used. Furthermore, a torsional rigidity is realized by a suitable design of the components, which minimizes the damage of components in the drive train in case of overload.
- the torsional vibration damper may comprise a centrifugal pendulum device.
- a centrifugal pendulum device can serve to improve the effectiveness of the torsional vibration damper.
- the centrifugal pendulum device can be arranged radially within the at least one energy store.
- the centrifugal pendulum device can be arranged axially between the flange portion and the cover portion of the input part.
- the centrifugal pendulum device may be arranged on the output part.
- the centrifugal pendulum device may have a pendulum mass carrier part.
- the flange part of the output part can serve as a pendulum mass carrier part.
- the centrifugal pendulum device may have at least one pendulum mass. The at least one pendulum mass can on the pendulum mass carrier part along a
- Pendulum be arranged displaced.
- the at least one pendulum mass can be displaced under centrifugal force in an operating position. In the operating position, the at least one pendulum mass can oscillate along the pendulum track in order to eliminate torsional vibrations.
- the at least one pendulum mass can oscillate starting from a middle position between two end positions.
- the stops of the additional flange can also interact on the input side with a primary flywheel at torsional vibration dampers without centrifugal pendulum device.
- torsional vibration dampers without centrifugal pendulum device attachment points can also be provided on a cover plate or a support plate.
- a failure of the energy storage is avoided.
- a failure of a bow spring is avoided.
- damage to components is avoided or at least minimized.
- a driveability of a motor vehicle is ensured in the event of a failure of the energy store.
- a stoppage of a motor vehicle is due to damage to the torsional vibration damper. prevents.
- a disruption of a drive train is prevented.
- a favorable impact design of secondary attacks is optimized.
- a load is reduced by impact forces.
- Fig. 1 shows a torsional vibration damper 100.
- the torsional vibration damper 100 is used in the present case for arrangement in a drive train of a motor vehicle between an internal combustion engine and a friction clutch device, for example as a dual-mass flywheel or dual-clutch damper.
- the torsional vibration damper 100 has an input part 102 and an output part 104.
- the torsional vibration damper 100 has an axis of rotation 106 about which the input part 102 and the output part 104 are rotatable together and limited relative to each other rotatable.
- spring springs 108 act as energy stores.
- the torsional vibration damper 100 has two approximately semi-circular arc-shaped bow springs 108.
- the bow springs 108 are designed as high-capacity springs and have an increased twist spacing.
- the bow springs 108 store energy or emit energy.
- a Friction device effective between the input part 102 and the output part 104 .
- the input part 102 has a flange portion 1 10 and a cover portion 1 12.
- the lid portion 1 12 has an annular disk-like shape.
- Flange portion 1 10 and the lid portion 1 12 are welded together.
- the flange portion 1 10 and the lid portion 1 12 define a torus-shaped receiving space for the bow springs 108.
- the input part 102 has projecting into the receiving space primary stops for input part-side support of the bow springs 108.
- the primary stops of the input part 102 are arranged axially opposite one another in each case on the flange section 110 and on the cover section 112.
- the lid section 1 12 has two primary stops 1 14, 1 16.
- the primary stops 1 14, 1 16 are arranged diametrically opposite one another.
- the primary stops 1 14, 1 16 are each designed as a through position.
- the primary stops 1 14, 1 16 are local areas of the lid portion 1 12, which are each formed from the material of the lid portion 1 12 against a cross-sectional curvature in the receiving space inside.
- the input part 102 has secondary stops 1 18, 120.
- the secondary stops 1 18, 120 of the input part 102 are arranged on the lid portion 1 12.
- the lid section 1 12 has two secondary stops 1 18, 120.
- the secondary stops 1 18, 120 are arranged diametrically opposite one another.
- the secondary stops 1 18, 120 are in the circumferential direction of the lid portion 1 12 centrally between the primary stops 1 14, 1 16 arranged. In the present case, the secondary stops 1 18, 120 to the primary stops 1 14, 1 16 offset by 90 °.
- the lid portion 1 12 has a substantially circular recess.
- the circular shape of the recess is interrupted by the secondary stops 1 18, 120.
- the recess is concentric with the axis of rotation 106.
- the secondary collars 1 18, 120 are radially aligned fingers which extend in the radial direction into the recess.
- the secondary stops 1 18, 120 are made in one piece with the lid portion 1 12.
- the secondary stops 1 18, 120 are radially further inside is arranged as an effective radius of the bow springs 108. In perennialsnchtung each of the two secondary stops 1 18, 120 is limited by two stop surfaces.
- the output part 104 has a flange part 122 and a flywheel part not shown in the figures.
- the flange portion 122 has radially outwardly into the receiving space projecting flange wings.
- the flange wings serve as primary impacts for output part-side support of the bow springs 108.
- the flange part 122 and the flywheel mass part are riveted together with the interposition of an additional flange 128.
- the output part 104 has the additional flange 128 with two secondary stops 124, 126.
- the secondary stops 124, 126 of the output part 104 are thus formed by the additional flange 128.
- the additional flange 128 is disposed in the axial direction between the flange portion 122 and the flywheel member and riveted thereto.
- the additional flange 128 consists of two flange segments 130,
- FIG. 2 shows a flange segment 130 as an individual part.
- the two flange segments 130, 132 are mirror-symmetrical with respect to a mirror plane in which the axis of rotation 106 is arranged.
- Each flange segment 130, 132 consists of a base body 134, 136, a first stop wing 138, 140 and a second stop wing 142, 144.
- Each first base 134, 136 is flat and curved around the axis of rotation 106.
- Two through holes in the basic bodies 134, 146 serve for riveting with the flange part 122 and the flywheel mass part.
- each base 134, 136 has two end portions in which it tapers in the radial direction and merges into one of the stop wings 138, 140, 142, 144.
- the stop wings 138, 140, 142, 144 are flat, finger-shaped areas of the
- the Flange segments 130, 132 which extend approximately in the radial direction.
- the two first stop wings 138, 140 are circumferentially adjacent and form a secondary stop 124 of the output part 104.
- the two second stop wings 142, 144 are circumferentially adjacent and form the other secondary stop 126 of the output part 104.
- each of the two secondary stops 124, 126 is formed by two stop wings 138, 140, 142, 144, the secondary stops 124, 126 have a lower rigidity than a one-piece secondary stop of the same size.
- the secondary stops 124, 126 can thereby avoid or at least minimize damage to components in the drive train in an overload situation.
- the secondary stops 124, 126 are arranged radially further inside than the effective radius of the bow springs 108.
- the secondary collisions 124, 126 are arranged diametrically opposite one another.
- the ends of the stop wings 138, 140, 142, 144 are remote from the axis of rotation 106.
- the secondary stops 124, 126 of the output part 104 are arranged in the same plane as the secondary stops 1 18, 120 of the input part 102. In the radial direction, the trajectories of the stop wings 138, 140, 142, 144 of the secondary stops 124, 126 of the output part 104 overlap with the Trajectories of the secondary stops 1 18, 120 of the input part 102, so that a relative rotation between the input part 102 and the output part 104 is limited possible.
- the bow springs 108 are based on the one hand on the primary stops 1 14, 1 16 of the input part 102 and on the other hand on the primary stops of the output part 104 from. Upon rotation of the input part 102 and the output part 104 relative to each other, the bow springs 108 are compressed or relaxed. In a regular operation, the bow springs 108 are actuated in their elastic range, the secondary stops 1 18, 120 of the input part 102 and the Sekundärran- strikes 124, 126 of the output part 104 do not come into contact.
- the input part 102 and the output part 104 are rotated relative to one another such that the secondary stops 18, 120 of the input part 102 and the secondary stops 124, 126 of the output part 104 come into contact before the turns of the bow springs 108 touch each other. Then there is an immediate mechanical power transmission between the input part 102 and the output part 104 without the interposition of the bow springs 108, the torsional vibration damper 100 is rigidly connected without the bow springs 108 are on block. The bow springs 108 are thereby less heavily loaded and the torsional vibration damper 100 is designed impact-resistant. LIST OF REFERENCES
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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
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102015203105.5A DE102015203105B4 (en) | 2015-02-20 | 2015-02-20 | torsional vibration dampers |
PCT/DE2016/200093 WO2016131457A1 (en) | 2015-02-20 | 2016-02-12 | Torsional vibration damper |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3259490A1 true EP3259490A1 (en) | 2017-12-27 |
Family
ID=55484788
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP16708350.0A Withdrawn EP3259490A1 (en) | 2015-02-20 | 2016-02-12 | Torsional vibration damper |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP3259490A1 (en) |
CN (1) | CN107208735B (en) |
DE (2) | DE102015203105B4 (en) |
WO (1) | WO2016131457A1 (en) |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102018111162A1 (en) | 2017-05-17 | 2018-11-22 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper and method of manufacturing a torsional vibration damper |
FR3069602B1 (en) * | 2017-07-28 | 2020-08-28 | Valeo Embrayages | SHOCK ABSORBER WITH ELASTIC LIMIT STOP |
FR3069600B1 (en) * | 2017-07-28 | 2020-07-03 | Valeo Embrayages | TORSION SHOCK ABSORBER WITH ELASTIC LIMIT STOP |
FR3069603B1 (en) * | 2017-07-28 | 2019-08-23 | Valeo Embrayages | TORSION SHOCK ABSORBER WITH ELASTIC END LIMIT STOP |
WO2019020808A2 (en) * | 2017-07-28 | 2019-01-31 | Valeo Embrayages | Torsional vibration damper with elastic end-stop |
DE102018104135B4 (en) * | 2018-02-23 | 2020-02-20 | Schaeffler Technologies AG & Co. KG | Pulley decoupler having a centrifugal pendulum device with a first friction device |
DE102018108404A1 (en) * | 2018-04-10 | 2019-10-10 | Schaeffler Technologies AG & Co. KG | torsional vibration dampers |
WO2021043363A1 (en) * | 2019-09-02 | 2021-03-11 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper having a centrifugal pendulum absorber and pre-damper |
DE102020202182A1 (en) | 2020-02-20 | 2021-08-26 | Zf Friedrichshafen Ag | Torsional vibration damper with angle of rotation limitation and clutch disc with torsional vibration damper |
DE102021202297A1 (en) | 2021-03-10 | 2022-09-15 | Zf Friedrichshafen Ag | Vehicle, dual mass flywheel and torque transfer device |
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DE19522718B4 (en) * | 1994-07-01 | 2009-07-30 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | torsional vibration damper |
JPH0949531A (en) * | 1995-08-08 | 1997-02-18 | Exedy Corp | Viscosity resistance generating mechanism |
US6035993A (en) * | 1999-02-26 | 2000-03-14 | Eaton Corporation | Friction clutch with pre-damper |
DE10133694A1 (en) * | 2000-07-27 | 2002-02-07 | Luk Lamellen & Kupplungsbau | Torsional vibration damper with transmission elements on both sides has intermediate element between control regions and circumferential ends of energy store |
GB2413615A (en) * | 2004-05-01 | 2005-11-02 | Safe Developments Ltd | A clutch friction plate assembly |
CN2871973Y (en) * | 2006-03-06 | 2007-02-21 | 山东理工大学 | Rigid-variable torsional vibration reducer of clutch of automobile |
WO2008106926A1 (en) * | 2007-03-08 | 2008-09-12 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Torsional vibration damper |
DE102008018218A1 (en) * | 2007-05-07 | 2008-11-13 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Divided flywheel, for an internal combustion motor, has a secondary inertia mass with springs and a primary limit working with an overload safety unit |
FR2918141B1 (en) * | 2007-06-26 | 2014-04-04 | Valeo Embrayages | TORSION OSCILLATION DAMPING DEVICE, IN PARTICULAR FOR A FRICTION CLUTCH, FOR EXAMPLE FOR A MOTOR VEHICLE. |
DE102013221655A1 (en) * | 2013-10-24 | 2015-04-30 | Schaeffler Technologies Gmbh & Co. Kg | torsional vibration dampers |
-
2015
- 2015-02-20 DE DE102015203105.5A patent/DE102015203105B4/en active Active
-
2016
- 2016-02-12 CN CN201680008419.9A patent/CN107208735B/en active Active
- 2016-02-12 EP EP16708350.0A patent/EP3259490A1/en not_active Withdrawn
- 2016-02-12 WO PCT/DE2016/200093 patent/WO2016131457A1/en active Application Filing
- 2016-02-12 DE DE112016000810.4T patent/DE112016000810A5/en not_active Withdrawn
Also Published As
Publication number | Publication date |
---|---|
WO2016131457A1 (en) | 2016-08-25 |
DE112016000810A5 (en) | 2017-11-16 |
DE102015203105B4 (en) | 2017-12-14 |
DE102015203105A1 (en) | 2016-08-25 |
CN107208735A (en) | 2017-09-26 |
CN107208735B (en) | 2019-11-15 |
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