WO2017194053A1 - Disque de friction pour amortisseur de disque d'embrayage - Google Patents

Disque de friction pour amortisseur de disque d'embrayage Download PDF

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Publication number
WO2017194053A1
WO2017194053A1 PCT/DE2017/100387 DE2017100387W WO2017194053A1 WO 2017194053 A1 WO2017194053 A1 WO 2017194053A1 DE 2017100387 W DE2017100387 W DE 2017100387W WO 2017194053 A1 WO2017194053 A1 WO 2017194053A1
Authority
WO
WIPO (PCT)
Prior art keywords
friction
spring
spring element
disc
flange
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/DE2017/100387
Other languages
German (de)
English (en)
Inventor
Oswald Friedmann
Wolfgang Haas
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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 Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Priority to DE112017002393.9T priority Critical patent/DE112017002393A5/de
Publication of WO2017194053A1 publication Critical patent/WO2017194053A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/60—Clutching elements
    • F16D13/64—Clutch-plates; Clutch-lamellae
    • F16D13/68—Attachments of plates or lamellae to their supports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/129—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/22—Vibration damping

Definitions

  • the invention relates to a friction disc for a clutch disc damper, with the help of a frictional damping for the clutch disc damper can be achieved.
  • a clutch disc damper in which an input flange connected to a clutch disc and composed of two cover discs is coupled via helical compression springs to an output flange connected to a transmission input shaft.
  • the output flange is designed in two parts, wherein between the two parts of the output flange a relatively limited rotatable friction disc is provided.
  • a friction disk for frictional damping in a clutch disk damper is provided with a friction ring for frictional engagement Located on an input flange or output flange of the clutch disc damper, a mounting portion for non-rotatable mounting with the rotatable relative to the friction ring output flange or input flange of the clutch disc damper and at least one rich with the friction ring and with the fastening ungsbe- coupled spring element to provide a compliance in the radial direction, the Friction ring is movable by the at least one spring element in all radial directions relative to the mounting area.
  • the input flange, the output flange and acting on the input flange and the output flange, designed in particular as a helical compression spring energy storage element of the clutch disc damper form a spring-mass system that can dampen torsional vibrations in the speed of the input flange.
  • a conscious frictional damping can be introduced into this spring-mass system, which can dampen a resonance-induced rocking of the torsional vibrations in the natural frequency range of the spring-mass system. Resonance-induced noise developments can be avoided.
  • the friction disc can be indirectly or directly connected to the input flange and thereby rub indirectly or directly on the limited rotatable to the input flange output flange.
  • the friction disc can be indirectly or directly connected to the output flange and thereby rub indirectly or directly on the limited rotatable to the output flange input flange.
  • the friction ring By means of the at least one spring element of the friction disk, however, it is possible for the friction ring to be connected movably in the radial direction. It is assumed that thereby the frictional force applied by the friction ring and an associated frictional torque can at least partially compensate for an uneven force distribution on the clutch disc, so that the force distribution on the clutch disc in the circumferential direction can be made uniform. Studies have shown that a soft connection of the clutch disc to the transmission input shaft in the radial direction can prevent high-frequency noise developments in the form of a "screech" or "eeken". The radial compliance of the friction ring can make a contribution to this. By achieved by means of the spring element radial compliance of the friction ring of the friction disc high-frequency noise developments when coupling a clutch disc can be avoided, so that a drive train of a motor vehicle with low noise developments is possible.
  • the friction disc can be coupled in motion with a component of the clutch disc damper.
  • the attachment area can be rotatably coupled via a toothing with the clutch disc or a transmission input shaft, with which the input flange or the output flange of the clutch disc damper is rotatably connected.
  • the attachment region is indirectly or directly fixed, for example via a rivet connection with the input flange or with the output flange.
  • the friction ring may abut against a component which is rotatable relative to the component with which the fastening region is connected or at least coupled in a manner such that friction-related relative rotation can take place.
  • the friction ring may, in the event of rotational nonuniformity, when the input flange rotates to a limited extent relative to the output flange, rub indirectly or indirectly restrictably at the output flange or the input flange to provide the friction damping.
  • the spring element can be supported on the one hand on the friction ring and on the other hand on the attachment area.
  • the spring element can in the direction of force of the spring element between the friction ring and the Mounting area to be connected in series.
  • a plurality of spring elements is provided, each of which allow a compliance in a specific radial direction, wherein the plurality of spring elements are arranged uniformly distributed in particular in the circumferential direction.
  • the at least one spring element is designed to support a frictional torque to be expected on the friction ring at the fastening region.
  • the spring element can be made sufficiently stiff in the tangential direction and / or in the circumferential direction.
  • a deliberate clearance angle of the friction ring in the circumferential direction relative to the component with which the fastening region is attached are provided via the spring element, so that at low rotational nonuniformities a frictional damping is avoided. This allows the frictional damping to take effect only at larger amplitudes.
  • allows the spring element to a rotational axis of the clutch disc damper which corresponds to the axis of rotation of the friction disc at a constant speed without rotational irregularities, a radial mobility of the friction ring of 0.5 mm
  • the spring element is designed to be rigid in the tangential direction and / or in the circumferential direction, wherein in particular the spring element has a spring constant c r in the radial direction and a spring constant c t in the tangential direction and 100 ⁇ Ct / c r ⁇ 3000, in particular 200 ⁇ Ct / c r ⁇ 2000, preferably
  • the spring constant Ct in the tangential direction may be, for example, 2000 N / mm ⁇ 500 N / mm.
  • the spring constant c r in the radial direction can be, for example, 1 N / mm to 10 N / mm.
  • the spring element in the tangential direction and / or in the circumferential direction at least until the beginning of a buckling failure, carried out substantially rigid.
  • the spring element has in the tangential direction and / or in the circumferential direction compared to the compliance in the radial direction only a low compliance, if any.
  • the friction ring can already be used at low force ratios in dodge dialer direction.
  • the friction ring is movable at a friction force determining normal force of greater than 15 N, preferably greater than 10 N and particularly preferably greater than 5 N in the radial direction.
  • a friction torque of more than 5 Nm, in particular up to 30 Nm, preferably of more than 10 Nm, in particular up to 20 Nm can be supported at the same time essentially free of play in the circumferential direction at the attachment area.
  • the friction ring, the attachment region and the spring element are made in one piece. The number of components of the clutch disc damper is thereby kept low.
  • the friction disk can be produced inexpensively by punching and non-cutting forming.
  • a first spring element in particular an opposing pair of two first spring elements, for providing a radial compliance in a first radial direction and a second spring element, in particular an opposite pair of two second spring elements, for providing a radial compliance in a second perpendicular to the first radial direction Radial direction provided.
  • the individual spring element essentially only needs to provide the desired flexibility in a radial direction, since the compliance in a radial direction rotated by 90 ° is provided by another spring element.
  • the single spring element can be constructed particularly simple.
  • the friction ring is connected to the fastening area via the first spring element and the second spring element connected in series to the first spring element, wherein a connecting piece is connected to the first spring element and the second spring element, wherein the connecting piece has in particular a ring-shaped closed support ring ,
  • the at least one spring element is designed as a, in particular substantially tangential, leaf spring.
  • the spring element is characterized in the radial direction very soft and can easily give way in the radial direction if necessary.
  • the spring element designed as a leaf spring can essentially act as a rod, which is essentially rigid and unyielding until the onset of buckling failure, and has at least a significantly lower flexibility than in the radial direction.
  • the respective spring element has more than one leaf spring, which, for example, connect the fastening region with the friction ring as substantially parallel strips.
  • the leaf springs are oriented such that they are claimed in the transmission of a friction torque essentially only to train. As a result, bending stresses that could lead to a buckling load can be avoided.
  • the attachment region for rotationally fixed attachment has an internal toothing or an external toothing or a passage opening.
  • the fastening region can easily be connected non-rotatably via a positive fastening and / or with the aid of a fastening means, for example a rivet connection or screw connection.
  • a passage window for passing a in particular designed as a helical compression spring, energy storage element for limited rotatable coupling of the input flange with provided the output flange.
  • the friction disk can extend into a radius region of the energy storage element of the clutch disk damper.
  • the friction disk can be ensured that enough space remains for the energy storage element and accidental impact of the energy storage element is avoided on the friction disc.
  • the invention further relates to a clutch disk damper for damping torsional vibrations of a clutch disk, comprising an input flange, in particular composed of two cover disks, for introducing a torque generated in a motor vehicle engine, a starting flange which is rotatable relative to the input flange, in particular between the cover disks Discharging the torque to a transmission input shaft, an engageable at the input flange and the output flange, in particular configured as a helical compression spring, energy storage element and at least one co-rotating with the input flange or with the output flange friction disc, which may be as described above and further educated, to provide a frictional force on the rotatable relative to the friction disc output flange or input flange.
  • a force acting on the friction disc designed in particular as a plate spring, friction spring for providing the frictional force to the friction disc is provided.
  • the spring force of the friction spring the normal force can be adjusted with which the friction ring of the friction disc acts on its friction partner. As a result, the frictional damping effect can be easily adjusted.
  • the friction spring is preferably supported on the output flange or input flange rotatable relative to the friction disk and an intermediate piece, wherein the intermediate piece acts on the axial side of the friction disk facing away from the friction spring and the friction disk acts on the friction spring between the intermediate piece and relative to the friction disk rotatable output flange or input flange is pressed.
  • the intermediate piece can preferably rotate at the same speed as the component on which the friction spring is supported with its other side. A wear-related relative rotation of the friction spring can be avoided.
  • the friction spring can compress the friction ring of the friction disk between the intermediate piece and the component on which the friction spring is supported with its other side, the friction ring can exert on its two axial sides a frictional relative rotation, whereby the frictional damping effect can be improved.
  • the intermediate piece can embrace the friction disk and the component on which the friction spring is supported with its other side.
  • the intermediate piece has a U-shaped cross-section, at the one radially projecting leg engage the friction spring and the other leg of the friction ring, wherein the two radially projecting legs are connected to each other via an axially extending base.
  • two or more friction disks are stacked in the axial direction one behind the other.
  • the friction disks can thereby each be inexpensively manufactured from a correspondingly thin single sheet and be layered in the axial direction.
  • the individual friction disks can be assembled to form a common friction flange.
  • the individual friction disks for example by different clearance angles in the circumferential direction provided for the individual friction disks, can perform a relative rotation relative to one another, whereby the friction-impairing damping effect is increased.
  • 1 is a schematic sectional view of a clutch disc damper
  • FIGS. 1 and 2 shows a schematic plan view of a friction disk of the clutch disk damper from FIGS. 1 and
  • FIG. 3 shows an alternative embodiment of a friction disc.
  • the clutch disk damper 10 shown in FIG. 1 has an input flange 14 which is connected to a clutch disk of a friction clutch for coupling a drive shaft of an automobile engine to a transmission input shaft 12 of a motor vehicle transmission, which in the illustrated embodiment is provided by a first cover disk 16 and one with the first cover disk 16 For example, connected via spacer bolts second cover plate 18 is composed.
  • the input flange 14 is coupled via an energy storage elements designed as a helical compression springs 20 with a limited to the input flange rotatably output flange 22 in order to damp by the thus formed spring-mass system Drehun- uniformities in the speed of the clutch disc.
  • the input flange 14, in particular the first cover disk 16 can be riveted to the clutch disk, while the output flange 22 can be non-rotatably connected to the transmission input shaft 12 via splines.
  • a friction disk 24 is provided.
  • the friction plate 24 is secured to the output flange 22, so that the friction plate 24 can perform a relative rotation to the input flange 14 at a rotational nonuniformity.
  • the friction disc 24 is pressed by means of a friction spring 26 against the second cover plate 18 of the input flange 14. Additionally or alternatively, a second friction disk may be pressed against the first cover disk 16.
  • the friction disc 24 may be connected to the input flange 16 and a relative rotation to the Run output flange 22.
  • a friction disk 24 may be connected to the first cover disk 16 and / or a friction disk 24 to the second cover disk 18.
  • designed as a plate spring friction spring 26 is supported on a force edge on the input flange 14 and the other edge of force on a radially projecting first leg 28 of an intermediate piece 30.
  • the intermediate piece 30 can grip around the friction disk 24 and the second cover disk 18 from radially inward so that the friction disk 24 can rub against the second cover disk 18 on one axial side and on a radially projecting second leg 32 of the intermediate piece 30 on the other axial side.
  • the friction disc 24 has a friction ring 34, which produces the frictional contact with the second cover plate 18 and the second leg 32.
  • the friction disk 24 also has attachment regions 36, by way of which the friction disk 24 can be riveted to the output flange in the illustrated embodiment. Radially within the friction disc 34 thereby remains sufficient space to provide for the clutch disc damper 10 an additional predamper can.
  • a first spring element 38 connects, which has several, for example, three, leaf springs 40 in the illustrated embodiment.
  • the leaf springs 40 of the first spring element 38 extend substantially in the tangential direction, so that a high resilience of the first spring element 38 along a first radial direction is given, while in the tangential direction and / or in the circumferential direction is given a low compliance.
  • the first spring element 38 is soft along the first radial direction and rigid in the tangential direction and / or in the circumferential direction or even rigid.
  • a second spring element 44 is connected via a connecting piece 42, which is finally connected to the friction ring 34.
  • the second spring element 44 has analogous to the first spring element 38 also tangentially extending blade remotes 40, which are aligned to the leaf spring 40 of the first spring element 38 rotated by 90 °.
  • the second spring element 44 is soft along the second radial direction and rigid in the tangential direction and / or in the circumferential direction or even rigid.
  • the spring elements 38, 44 can thereby allow a mobility of the friction ring 34 in the radial plane even at low forces, so that high-frequency noise developments when coupling the clutch disc can be avoided.
  • the friction ring 34 is substantially torsionally rigid connected to the mounting portion 36, so that a high friction torque can be supported.
  • the connecting pieces 42 are integrally connected to one another via a ring-shaped closed support ring 46.
  • the support ring 46 extends radially outward into the radius region of the energy storage element 20.
  • passage windows 48 are provided in the support ring 46, through which the respective energy storage element 20 can protrude.
  • the friction disc 24 is configured in one piece, so that the entire friction disc 24 can be produced inexpensively by punching and non-cutting forming of a metal sheet.
  • the friction ring 34 is provided radially on the outside and the fastening region 36 is provided radially on the inside.
  • the attachment region 36 can be connected to the transmission input shaft 12 in a rotationally fixed manner, for example, via an internal toothing, so that the attachment region 36 is connected to the output flange 22 of the clutch disk damper 10 in a torque-proof manner indirectly via the transmission input shaft 12.
  • first spring element 38 and the second spring element 44 each have only one leaf spring 40.
  • the ring is closed as a ring Support ring 46 configured connecting piece 42 is provided in the radial direction between the first spring element 38 and the second spring element 44, while in the embodiment of the friction disc 24 shown in FIG. 2, the first spring element 38 and the second spring element 44 are arranged on a common central radius.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un disque de friction (24) pour l'amortissement en friction dans un amortisseur de disque d'embrayage (10), comportant une bague de friction (34) portant en contact de friction sur une bride d'entrée (14) ou une bride de sortie (22) de l'amortisseur de disque d'embrayage (10), une partie fixation (36) pour la fixation bloquée en rotation à la bride de sortie (22) ou à la bride d'entrée (14) de l'amortisseur de disque d'embrayage (10) rotative par rapport à la bague de friction (34), et au moins un élément élastique (38, 44) raccordé à la bague de friction (34) et à la partie fixation (36) pour assurer une flexibilité en direction radiale, la bague de friction (34) pouvant être déplacée par le ou les éléments élastiques (38, 44) dans toutes les directions radiales par rapport à la partie fixation (36). La flexibilité radiale de la bague de friction (34) du disque de friction (24) obtenue au moyen de l'élément ressort (38, 44) permet d'éviter la génération de bruit lors de l'accouplement d'un disque d'embrayage de sorte qu'il soit possible de réaliser une chaîne cinématique de véhicule automobile générant peu de bruit.
PCT/DE2017/100387 2016-05-11 2017-05-08 Disque de friction pour amortisseur de disque d'embrayage Ceased WO2017194053A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112017002393.9T DE112017002393A5 (de) 2016-05-11 2017-05-08 Reibscheibe für einen Kupplungsscheibendämpfer

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016208120.9 2016-05-11
DE102016208120.9A DE102016208120A1 (de) 2016-05-11 2016-05-11 Reibscheibe für einen Kupplungsscheibendämpfer

Publications (1)

Publication Number Publication Date
WO2017194053A1 true WO2017194053A1 (fr) 2017-11-16

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ID=59061744

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2017/100387 Ceased WO2017194053A1 (fr) 2016-05-11 2017-05-08 Disque de friction pour amortisseur de disque d'embrayage

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DE (2) DE102016208120A1 (fr)
WO (1) WO2017194053A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112178125A (zh) * 2019-07-02 2021-01-05 舍弗勒技术股份两合公司 减振装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019100372A1 (de) * 2019-01-09 2020-07-09 Schaeffler Technologies AG & Co. KG Kupplungsscheibe mit einer Dämpfereinheit für eine Reibkupplung

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012214022A1 (de) 2012-08-08 2014-02-13 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer
DE102014212017A1 (de) * 2013-07-10 2015-01-15 Schaeffler Technologies Gmbh & Co. Kg Drehschwingungsdämpfer

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012214022A1 (de) 2012-08-08 2014-02-13 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer
DE102014212017A1 (de) * 2013-07-10 2015-01-15 Schaeffler Technologies Gmbh & Co. Kg Drehschwingungsdämpfer

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112178125A (zh) * 2019-07-02 2021-01-05 舍弗勒技术股份两合公司 减振装置

Also Published As

Publication number Publication date
DE112017002393A5 (de) 2019-01-17
DE102016208120A1 (de) 2017-11-16

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