WO2019192645A1 - Kupplungsscheibe mit reibeinrichtung aufweisendem pendelwippendämpfer; sowie reibkupplung - Google Patents
Kupplungsscheibe mit reibeinrichtung aufweisendem pendelwippendämpfer; sowie reibkupplung Download PDFInfo
- Publication number
- WO2019192645A1 WO2019192645A1 PCT/DE2019/100209 DE2019100209W WO2019192645A1 WO 2019192645 A1 WO2019192645 A1 WO 2019192645A1 DE 2019100209 W DE2019100209 W DE 2019100209W WO 2019192645 A1 WO2019192645 A1 WO 2019192645A1
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- WO
- WIPO (PCT)
- Prior art keywords
- friction
- relative
- clutch disc
- intermediate parts
- spring
- Prior art date
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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
- F16F15/129—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 characterised by friction-damping means
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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
- F16F15/1204—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
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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
- F16F15/123—Wound springs
- F16F15/1232—Wound springs characterised by the spring mounting
- F16F15/1234—Additional guiding means for springs, e.g. for support along the body of springs that extend circumferentially over a significant length
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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
- F16F2222/00—Special physical effects, e.g. nature of damping effects
- F16F2222/04—Friction
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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
- F16F2230/00—Purpose; Design features
- F16F2230/0052—Physically guiding or influencing
- F16F2230/0064—Physically guiding or influencing using a cam
-
- 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
- F16F3/00—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic
- F16F3/02—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic with springs made of steel or of other material having low internal friction
- F16F3/04—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic with springs made of steel or of other material having low internal friction composed only of wound springs
- F16F3/06—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic with springs made of steel or of other material having low internal friction composed only of wound springs of which some are placed around others in such a way that they damp each other by mutual friction
Definitions
- the invention relates to a clutch disc for a friction clutch of a motor vehicle, such as a car, truck, bus or other commercial vehicle, with an input part rotatable about an axis of rotation, having a friction lining, an output part likewise rotatable about the axis of rotation and the input part
- the pendulum rocker damper coupled to the output part, the pendulum rocker damper furthermore having a first flange region connected to the input part, a second flange region connected to the output part and rotatable about the rotational axis in a limited angular range relative to the first flange region, and two each via one Sliding link having with the two Flansch Schemeen motion-coupled intermediate parts, and wherein a spring unit cooperates with the link devices such that in a relative rotation of the flange to each other go a relative movement of the intermediate parts toward each other through the spring unit emmt / supported.
- the invention relates to a friction clutch for a drive train of a
- DE 10 2015 211 899 A1 discloses a torsional vibration damper with an input part arranged around an axis of rotation and an input part rotatable relative to the input part about the axis of rotation and counter to the action of a spring device.
- EP 1 602 854 A2 discloses a device for absorbing torque fluctuations.
- a friction device is arranged inside or outside a spring element of the spring unit and has the effect that a higher relative force of the intermediate parts inhibiting frictional force is generated by the friction device in a first relative movement range of the intermediate parts to the first movement range offset second relative range of motion of the intermediate parts.
- a friction device is selectively used to generate a position-dependent friction force.
- the spring element (the spring unit) clamped between a first intermediate part and a second intermediate part is designed as a helical compression spring, the spring element is made particularly compact.
- the friction device to a radial outer side of the spring element, with respect to a longitudinal extent / longitudinal axis of the Federele- mentes, or to a radial inner side of the spring element, with respect to the Longitudinal extension / longitudinal axis of the spring element, is arranged.
- the entire clutch disc can then also be made particularly compact.
- the friction device has a first friction element fastened to the first intermediate part and a second friction element fastened to the second intermediate part and frictionally engages with the first friction element over the first movement region of the intermediate parts, the friction device is special easy to set up.
- the first friction element in a transverse direction of the spring element (/ transverse to the longitudinal extent) is rigid / non-deformable / inflexible and the second friction element is deformable (elastically) relative to the first friction element in the transverse direction of the spring element, the first friction element is particularly simple. adjustable.
- the second friction element is particularly preferably equipped with at least one deformable in the transverse direction of the spring element friction arm, which abuts (rubbing) in the first relative movement range of the intermediate parts on a side surface (preferably a radial outer surface) of the first friction element.
- the friction arm preferably abuts on the side surface of the first friction element under a radial pretension.
- the side surface of the first friction element narrows / reduces in diameter toward the second intermediate part.
- the second friction element is more preferably formed as a pin or a sleeve, so that it cleverly radially within the spring element (in the embodiment as a pin) or radially outside to the spring element around (when designed as a sleeve), arranged to save space. Furthermore, it is advantageous if the (first and second) friction elements are matched to one another in such a way that they are spaced apart from one another in the second relative movement range of the intermediate parts, ie the friction device is deactivated in the second relative movement range (friction force generated by Friction device is generated is minimal / zero). As a result, the friction device is further improved in its wear behavior.
- the first friction element is composed of a plurality of longitudinal regions which differ in terms of their friction coefficients.
- the different friction coefficients are particularly preferably implemented by different materials.
- the first friction element is formed over its extension along the longitudinal axis (in a plurality of adjoining longitudinal regions) by different materials.
- the second friction element consists of metal in the longitudinal direction, such as steel, or of plastic of the polyamide type with an admixture of carbon fibers, Teflon and / or graphite.
- the frictional force is adjusted particularly cleverly as a function of the first relative movement range of the intermediate parts.
- the invention relates to a friction clutch for a drive train of a motor vehicle, with a pressure plate and, with the pressure plate frictionally engageable, clutch disc according to the invention according to at least one of the embodiments described above.
- a clutch disc is realized with pendulum rocker damper with hysteresis device (friction device). It is proposed to provide at least one spring (spring element) of the pendulum rocker damper with a friction device for generating a position-dependent friction force, wherein the friction device is arranged inside or outside the spring.
- FIG. 1 is a perspective view of a clutch disc according to the invention according to a first embodiment, wherein the basic structure of a built-in clutch disc pendulum rocker is clearly visible,
- FIG. 2 shows a cross-sectional view of a region of the PTO rocker damper used in FIG. 1, wherein the structure of a clean device acting together with a spring unit between two intermediate parts of the pendulum rocker damper can be seen,
- FIG. 3 is a perspective view of the transversely cut portion of the pendulum rocker dam shown in FIG. 2; FIG.
- Fig. 4 is a cross-sectional view of a portion of a pendulum rocker damper, as used in a clutch disc according to the invention according to a second embodiment, wherein the friction device in its formation of the friction device of the first embodiment differs such that it now arranged outside of a spring element of the spring unit is and
- FIG. 5 is a perspective view of the transversely sectioned portion of the pendulum rocker damper shown in FIG. 4.
- FIG. 5 is a perspective view of the transversely sectioned portion of the pendulum rocker damper shown in FIG. 4.
- a clutch disc according to the invention 1 according to a first exemplary embodiment in its basic structure to recognize.
- the clutch disc 1 is used in operation in a typical manner in a friction clutch and is accordingly with a pressure plate, not shown here for the sake of clarity, in operative connection.
- the clutch disk 1 in a closed position of the friction clutch, the clutch disk 1 is frictionally engaged with this pressure plate and freely rotatable relative to the pressure plate in an open position of the friction clutch.
- the friction clutch is again preferably arranged in a drive train of a motor vehicle, namely directly between an internal combustion engine and a transmission of the drive train along the torque transmission flow.
- the clutch disk 1 has an input part 4, an output part 5 and a pendulum-action rocker 6 acting between the input part 4 and the output part 5.
- the input part 4 has a friction lining support 19 and a friction lining 3 applied / fixed on this friction lining support 19.
- a friction lining 3 is arranged on each axial side of the friction lining carrier 19 (seen along an axis of rotation 2 of the clutch disk 1).
- the integral ring-shaped input part 4 is arranged rotatably about the rotation axis 2.
- an output part 5 is likewise rotatably arranged about the rotation axis 2.
- the output part 5 typically forms a hub 20 which, during operation, is rotatively connected to a shaft of the drive train (not shown here for the sake of clarity), such as a transmission input shaft of the transmission.
- the pendulum rocker damper 6 is typically used to dampen rotational nonuniformity of the drive train.
- a rotational irregularity usually occurring on the part of the internal combustion engine is typically introduced into the clutch disc 1 via the input part 4 and damped by the pendulum rocker damper 6 in the transmission path from the input part 4 to the output part 5.
- the pendulum rocker damper 6 has a first flange portion 7 which is rotatably connected to the input part 4.
- the Reibbelagango 19 is mounted directly to the first flange 7 in this embodiment, namely riveted.
- the first flange portion 7 is formed substantially annular disc-shaped.
- the pendulum rocker damper 6 has a second flange region 8, which is connected in a rotationally fixed manner to the output part 5.
- the second flange portion 8 is like the first flange portion 7 coaxial with and rotatably disposed about the rotation axis 2.
- the two flange portions 7 and 8 are in principle rotationally coupled to each other / rotatably connected, but in a limited angular range in a rotational direction about the rotation axis 2 relative to each other rotatable.
- the two flange regions 7 and 8 are coupled in motion / rotationally coupled to one another via two intermediate parts 11 a, 11 b.
- the two intermediate parts 11 a, 11 b are designed substantially as identical parts and arranged relative to each other in a radial direction of the rotation axis 2 slidably.
- the two intermediate parts 11 a, 11 b are offset by about 180 ° in the rotational direction about the rotation axis 2 relative to each other.
- Each (first and second) intermediate part 11a and 11b is coupled in a similar manner to the respective first flange region 7 and the second flange region 8 via a rocker device 9, 10.
- the first link device 9 serves as the first flange region 7 with the respective intermediate part 11 a and 11 b coupling device.
- the first link device 9 can be seen in FIG. 1 from two first slide tracks 21, which are introduced into the intermediate part 11 a, 11 b, and two roller bodies 22, which are slidably received in each of the first slide tracks 21.
- the roller bodies 22 of the first slide device 9 assigned to the first slide tracks 21 are also accommodated in the first flange area 7.
- the second link device 10 which movably couples the intermediate part 11 a, 11 b to the second flange section 8, is shown in FIG. 1 by a second link track 23, which is introduced into the second flange section 8.
- Another roller body 22 is slidably received in the second slide track 23.
- This roller body 22 is at the same time slidably received in a third slide track 24 introduced in the intermediate part 11 a, 11 b.
- the intermediate parts 11a, 11b are coupled to the flange areas 7, 8 via the slotted links 9, 10 such that, during operation, relative rotation of the flange areas 7, 8 relative to one another results in relative movement / displacement of the intermediate parts 11 a, 11 b according to the embodiment of the slide tracks 21, 23, 24 comes in a circumferential direction and in the radial direction.
- a spring unit 12 acts on the intermediate parts 1 1 a, 1 1 b.
- the spring unit 12 is (in the radial direction) between the intermediate parts 1 1 a, 1 1 b clamped such that it inhibits a displacement of the intermediate parts 1 1 a, 1 1 b relative to each other in the first movement direction and supported in the second direction of movement ,
- the spring unit 12 has two spring elements 14, only one of the two spring elements 14 being illustrated in FIG. 1 for the sake of clarity.
- the embodiment of both spring elements 14 is shown in FIGS. 2 and 3 continue to recognize.
- the two spring elements 14 are identical and equal to the intermediate parts 1 1 a, 1 1 b added. Only in terms of their position are the spring elements 14 different.
- the two spring elements 14 are arranged on opposite sides with respect to the axis of rotation 2.
- the respective spring element 14 is implemented as a helical compression spring.
- the helical compression spring 14 extends straight along a longitudinal axis 25, which extends in the circumferential direction as well as in the radial direction.
- a friction device 13 is now provided in the spring unit 12, namely per spring element 14.
- a total of two friction devices 13 are provided in the spring unit 12.
- the respective friction device 13 can be seen particularly clearly in FIG. 1 by recessing one of the two spring elements 14 in a perspective view.
- the friction device 13 acts on the relative movement of the intermediate parts 11a, 11b such that it generates a higher frictional force in a first relative movement region / displacement path / displacement section of the intermediate parts 11a, 11b as in an axially offset / adjacent to the first relative Movement area arranged / subsequent second relative movement range / displacement path / displacement section of the intermediate parts 11 a, 11 b. If the intermediate parts 11a, 11b, as seen in FIG.
- the friction device 13 is arranged radially inside the spring element 14 (that is to say radially within a longitudinal axis 25 of the spring element 14).
- the friction device 13 consists of two friction elements 15, 16.
- a first friction element 15, as in FIGS. 2 and 3 is particularly well recognized, is designed as a pin.
- the first friction element 15 is thus set pin-shaped / peg-shaped.
- the first friction element 15 is substantially rigid.
- the first friction member 15 is attached / fixedly attached to the first intermediate part 11a in this embodiment.
- the first friction element 15 extends from the first intermediate part 11a to the second intermediate part 11b.
- a second friction element 16 of the friction device 13 is attached to the second intermediate part 11 b / firmly attached.
- the second friction element 16 extends from the second intermediate part 11 b out to the first intermediate part 11 a.
- the second friction element 16 as can be seen in FIG. 1, is implemented overall in the form of a sleeve in the form of a sleeve.
- the second friction element 16 is likewise arranged (with respect to the longitudinal axis 25) radially inside the spring element 14, but radially outside the first friction element 15.
- the second friction element 16 has a plurality of axial slots 26.
- the second friction element 16 forms a plurality of friction arms 17 which can be deformed in the radial direction with respect to the longitudinal axis 25.
- the friction arms 17 interact directly with the first friction element 15.
- the friction arms 17 are in frictional contact with a side surface 18 (radial outer surface) of the first friction element 15 in the relative movement range of the intermediate parts 11 a, 11 b.
- the first friction element 15 is in principle designed so that in the relative movement of the intermediate parts 11 a, 11 b in the radial direction toward one another, ie in the first direction of movement and in the first range of motion to a constant increase in the frictional force between the friction elements 15, 16 is generated comes. On the one hand, this is due to the side surface 18 of the first friction element 15 which tapers towards the second intermediate part 11b, and on the other hand to the formation of the friction bar 17.
- the friction arms 17 are elastically biased inwards in the radial direction and thus lie inward in the radial direction biased on the side surface 18 at. With increasing movement of the intermediate parts 11 a, 11 b toward each other in the first direction of movement, the pressing force of the friction bar 17 increases towards the first friction element 15, so that in turn the frictional force correspondingly increases.
- the first friction element 15 seen in the axial direction, has various longitudinal regions which have a different coefficient of friction.
- the different coefficients of friction are formed by different materials / material properties.
- the first friction element 15 is formed in the axial direction with respect to the longitudinal axis 25 with a plurality of longitudinal regions of different materials.
- a first longitudinal region of the first friction element 15 is formed with a first material
- a second longitudinal region of the first friction element 15 is formed with a second material.
- the materials are, for example, plastic materials, such as polyamide, which is preferably reinforced with fibers.
- metal materials, such as steel may also be used as materials.
- FIGS. 4 and 5 a further second exemplary embodiment is illustrated, wherein in the two FIGS. 4 and 5, for the sake of clarity, again only one area of the pendulum rocker damper 6, as already shown in FIGS. 2 and 3, is shown.
- both the first friction element 15 and the second friction element 16 are sleeve-shaped.
- the first friction element 15 is realized as a rigid (non-deformable in the radial direction) dielse.
- the second friction element 16 in turn surrounds the first friction element 15 radially from the outside and bears against the side surface 18 of the first friction element 15 in the first relative movement range of the intermediate parts 10a, 10b.
- the two friction elements 15, 16 are also arranged radially outside the spring element 14.
- the first friction element 15 and the second friction element 16 thus continue to be, as already shown in FIGS. 1 to 3, arranged coaxially with the longitudinal axis 25, but extend in the radial direction from the outside around the spring element 14 around.
- the side surface 18 of the first friction element 15 further tapers along its extension in the axial direction toward the second intermediate part 11b.
- the two intermediate elements shift in one direction (axial direction with respect to the spring elements 14) and operate the intermediate compression springs (spring elements 14) in parallel.
- This relative axial movement is used to generate frictional force or hysteresis.
- the frictional force or the hysteresis is designed as a function of the angle of rotation.
- the design of the friction point is dependent on the installation space. A friction point around / outside or in / within the compression spring 14 is advantageous in some cases with respect to the volume of the torsion damper 6.
- a torsional vibration damper 6 of the pendulum rocker type is implemented such that two opposing intermediate elements 11a, 11b actuate the intermediate compression springs 14 in parallel, with a first element (first friction element 15) connected to a first intermediate element 11a rubs with the other second intermediate element 11 b connected resilient second element (second friction element 16).
- the resilient element 16 is elastically deformed relative to the first element 15 by the relative movement of the two intermediate elements 11 a, 11 b. Due to the radial excess between the elements 15, 16, a certain frictional force between the two elements 15, 16 occurs.
- the shape of the first element 15 is designed so that after the axial change in position of the intermediate elements 11a, 11b to each other or after a change in the angle of rotation of the pendulum rocker damper 6, the first element 15 deforms the second element 16 with a certain excess and so a certain frictional force or hysteresis occurs.
- the shape of the first element 15 is designed such that the hysteresis, after the axial change in position of the intermediate elements 11a, 11b, is switched off to one another or after a change in the angle of rotation of the pendulum rocker damper 6 can, by the two elements 15, 16 are no longer in contact.
- the first element 15 consists of steel and / or plastic of the polyamide type with admixture of carbon fiber, Teflon or graphite.
- the first element 15 is an assembly of two or more parts (longitudinal regions) made of different materials.
- the frictional force or the hysteresis is designed as a function of the angle of rotation.
- the elements 15, 16 are arranged in the pressure spring 14.
- the elements 15, 16 are arranged around the compression spring 14.
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2020554163A JP7146939B2 (ja) | 2018-04-05 | 2019-03-08 | 摩擦装置を有する振り子ロッカーダンパを有するクラッチディスク、ならびに摩擦クラッチ |
DE112019001759.4T DE112019001759A5 (de) | 2018-04-05 | 2019-03-08 | Kupplungsscheibe mit reibeinrichtung aufweisendem pendelwippendämpfer; sowie reibkupplung |
KR1020207027573A KR20200138232A (ko) | 2018-04-05 | 2019-03-08 | 마찰 장치를 가진 진자 로커 댐퍼를 구비한 클러치 디스크 및 마찰 클러치 |
CN201980008937.4A CN111630296B (zh) | 2018-04-05 | 2019-03-08 | 带有具备摩擦装置的摇臂式减振器的离合器从动盘以及摩擦离合器 |
EP19713349.9A EP3775606A1 (de) | 2018-04-05 | 2019-03-08 | Kupplungsscheibe mit reibeinrichtung aufweisendem pendelwippendämpfer; sowie reibkupplung |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE102018108049.2 | 2018-04-05 | ||
DE102018108049.2A DE102018108049A1 (de) | 2018-04-05 | 2018-04-05 | Kupplungsscheibe mit Reibeinrichtung aufweisendem Pendelwippendämpfer; sowie Reibkupplung |
Publications (1)
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WO2019192645A1 true WO2019192645A1 (de) | 2019-10-10 |
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PCT/DE2019/100209 WO2019192645A1 (de) | 2018-04-05 | 2019-03-08 | Kupplungsscheibe mit reibeinrichtung aufweisendem pendelwippendämpfer; sowie reibkupplung |
Country Status (6)
Country | Link |
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EP (1) | EP3775606A1 (de) |
JP (1) | JP7146939B2 (de) |
KR (1) | KR20200138232A (de) |
CN (1) | CN111630296B (de) |
DE (2) | DE102018108049A1 (de) |
WO (1) | WO2019192645A1 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102020105144A1 (de) | 2020-02-27 | 2021-09-02 | Schaeffler Technologies AG & Co. KG | Torsionsschwingungsdämpfer mit Reibeinrichtung |
US11940018B2 (en) | 2018-04-10 | 2024-03-26 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper |
DE102022133106A1 (de) | 2022-12-13 | 2024-06-13 | Schaeffler Technologies AG & Co. KG | Pendelwippendämpfer mit einer Rotationsachse für einen Antriebsstrang |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102020110889B4 (de) | 2020-04-22 | 2022-01-05 | Schaeffler Technologies AG & Co. KG | Torsionsschwingungsdämpfer mit koppelbarem Tilgersystem, sowie Antriebsstrang mit Torsionsschwingungsdämpfer |
DE102020127458A1 (de) * | 2020-08-14 | 2022-02-17 | Schaeffler Technologies AG & Co. KG | Pendelwippendämpfer mit einstellbarer Reibeinrichtung; sowie Hybridantriebsstrang |
DE102021102931B3 (de) * | 2021-02-09 | 2022-05-19 | Schaeffler Technologies AG & Co. KG | Pendelwippendämpfer mit einer Verdrehachse |
DE102021105447B3 (de) * | 2021-03-08 | 2022-06-23 | Schaeffler Technologies AG & Co. KG | Pendelwippendämpfer mit einer Verdrehachse |
DE102022117832B3 (de) | 2022-07-18 | 2023-11-09 | Schaeffler Technologies AG & Co. KG | Pendelwippendämpfer |
DE102022134120A1 (de) | 2022-12-20 | 2024-06-20 | Schaeffler Technologies AG & Co. KG | Torsionsschwingungsdämpfer |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2337134A (en) * | 1940-01-29 | 1943-12-21 | Thelander W Vincent | Clutch plate |
FR2371609A1 (fr) * | 1976-11-17 | 1978-06-16 | Ferodo Sa | Dispositif amortisseur de torsion notamment pour friction d'embrayage, en particulier de vehicule automobile |
JPS59212534A (ja) * | 1983-05-13 | 1984-12-01 | Daikin Mfg Co Ltd | ダンパ−デイスク |
EP1602854A2 (de) | 2000-07-27 | 2005-12-07 | Toyota Jidosha Kabushiki Kaisha | Vorrichtung zur Dämpfung von Drehmomentschwankungen mit einer Struktur zur Verringerung von Ausrichtungsfehlern des Drehmomentbegrenzers beim Zusammenbau |
DE102011105020A1 (de) * | 2010-06-29 | 2011-12-29 | Schaeffler Technologies Gmbh & Co. Kg | Torsionsschwingungsdämpfer |
WO2014135144A1 (de) * | 2013-03-05 | 2014-09-12 | Ulrich Rohs | Torsionsschwingungsdämpfer mit zumindest einer primärseite und einer sekundärseite |
WO2014202072A1 (de) * | 2013-06-21 | 2014-12-24 | Schaeffler Technologies Gmbh & Co. Kg | Drehmomentübertragungseinrichtung |
DE102015211899A1 (de) | 2015-06-26 | 2016-12-29 | Schaeffler Technologies AG & Co. KG | Torsionsschwingungsdämpfer |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2655698B1 (fr) * | 1989-12-12 | 1994-06-24 | Valeo | Dispositif amortisseur de torsion, notamment pour embrayages de vehicules automobiles. |
GB9803048D0 (en) * | 1998-02-13 | 1998-04-08 | Automotive Products Plc | A damping device |
DE19909044B4 (de) * | 1998-03-07 | 2018-06-21 | Schaeffler Technologies AG & Co. KG | Drehschwingungsdämpfer |
EP1496288B1 (de) * | 2003-07-07 | 2007-01-10 | BorgWarner Inc. | Torsionsschwingungsdämpfer |
WO2005028914A1 (ja) * | 2003-09-16 | 2005-03-31 | Exedy Corporation | 2マスフライホイール |
EP1668267B1 (de) * | 2003-09-22 | 2012-10-31 | Litens Automotive Partnership | Kurbelwellenentkuppler |
CN101086279A (zh) * | 2006-06-07 | 2007-12-12 | 卢克摩擦片和离合器两合公司 | 扭转振动减振装置 |
CN103210238B (zh) * | 2010-11-26 | 2015-03-11 | 丰田自动车株式会社 | 扭转振动衰减装置 |
JP6290944B2 (ja) * | 2015-02-20 | 2018-03-07 | 三ツ星ベルト株式会社 | プーリ構造体 |
CN105443657B (zh) * | 2015-11-29 | 2018-02-13 | 重庆元创汽车整线集成有限公司 | 干摩擦片式扭转减振器 |
-
2018
- 2018-04-05 DE DE102018108049.2A patent/DE102018108049A1/de not_active Withdrawn
-
2019
- 2019-03-08 DE DE112019001759.4T patent/DE112019001759A5/de active Pending
- 2019-03-08 JP JP2020554163A patent/JP7146939B2/ja active Active
- 2019-03-08 KR KR1020207027573A patent/KR20200138232A/ko not_active Application Discontinuation
- 2019-03-08 EP EP19713349.9A patent/EP3775606A1/de not_active Withdrawn
- 2019-03-08 WO PCT/DE2019/100209 patent/WO2019192645A1/de active Application Filing
- 2019-03-08 CN CN201980008937.4A patent/CN111630296B/zh active Active
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2337134A (en) * | 1940-01-29 | 1943-12-21 | Thelander W Vincent | Clutch plate |
FR2371609A1 (fr) * | 1976-11-17 | 1978-06-16 | Ferodo Sa | Dispositif amortisseur de torsion notamment pour friction d'embrayage, en particulier de vehicule automobile |
JPS59212534A (ja) * | 1983-05-13 | 1984-12-01 | Daikin Mfg Co Ltd | ダンパ−デイスク |
EP1602854A2 (de) | 2000-07-27 | 2005-12-07 | Toyota Jidosha Kabushiki Kaisha | Vorrichtung zur Dämpfung von Drehmomentschwankungen mit einer Struktur zur Verringerung von Ausrichtungsfehlern des Drehmomentbegrenzers beim Zusammenbau |
DE102011105020A1 (de) * | 2010-06-29 | 2011-12-29 | Schaeffler Technologies Gmbh & Co. Kg | Torsionsschwingungsdämpfer |
WO2014135144A1 (de) * | 2013-03-05 | 2014-09-12 | Ulrich Rohs | Torsionsschwingungsdämpfer mit zumindest einer primärseite und einer sekundärseite |
WO2014202072A1 (de) * | 2013-06-21 | 2014-12-24 | Schaeffler Technologies Gmbh & Co. Kg | Drehmomentübertragungseinrichtung |
DE102015211899A1 (de) | 2015-06-26 | 2016-12-29 | Schaeffler Technologies AG & Co. KG | Torsionsschwingungsdämpfer |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11940018B2 (en) | 2018-04-10 | 2024-03-26 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper |
DE102020105144A1 (de) | 2020-02-27 | 2021-09-02 | Schaeffler Technologies AG & Co. KG | Torsionsschwingungsdämpfer mit Reibeinrichtung |
WO2021170171A1 (de) | 2020-02-27 | 2021-09-02 | Schaeffler Technologies AG & Co. KG | Torsionsschwingungsdämpfer mit reibeinrichtung |
DE102020105144B4 (de) | 2020-02-27 | 2022-01-27 | Schaeffler Technologies AG & Co. KG | Torsionsschwingungsdämpfer mit Reibeinrichtung |
DE102022133106A1 (de) | 2022-12-13 | 2024-06-13 | Schaeffler Technologies AG & Co. KG | Pendelwippendämpfer mit einer Rotationsachse für einen Antriebsstrang |
Also Published As
Publication number | Publication date |
---|---|
EP3775606A1 (de) | 2021-02-17 |
DE112019001759A5 (de) | 2020-12-24 |
JP7146939B2 (ja) | 2022-10-04 |
KR20200138232A (ko) | 2020-12-09 |
JP2021519894A (ja) | 2021-08-12 |
DE102018108049A1 (de) | 2019-10-10 |
CN111630296A (zh) | 2020-09-04 |
CN111630296B (zh) | 2022-03-29 |
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