WO2019200418A1 - Disque d'embrayage - Google Patents

Disque d'embrayage Download PDF

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Publication number
WO2019200418A1
WO2019200418A1 PCT/AT2019/060126 AT2019060126W WO2019200418A1 WO 2019200418 A1 WO2019200418 A1 WO 2019200418A1 AT 2019060126 W AT2019060126 W AT 2019060126W WO 2019200418 A1 WO2019200418 A1 WO 2019200418A1
Authority
WO
WIPO (PCT)
Prior art keywords
friction
friction lining
elements
carrier
clutch disc
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/AT2019/060126
Other languages
German (de)
English (en)
Inventor
Stefan Astecker
Stefan Gaigg
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.)
Miba Frictec GmbH
Original Assignee
Miba Frictec GmbH
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 Miba Frictec GmbH filed Critical Miba Frictec GmbH
Priority to CN201980025959.1A priority Critical patent/CN111989504B/zh
Priority to DE112019001963.5T priority patent/DE112019001963A5/de
Publication of WO2019200418A1 publication Critical patent/WO2019200418A1/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
    • 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
    • F16D2013/642—Clutch-plates; Clutch-lamellae with resilient attachment of frictions rings or linings to their supporting discs or plates for allowing limited axial displacement of these rings or linings

Definitions

  • the invention relates to a clutch disc for a friction clutch, comprising a disc-shaped base body with a support member, wherein the support member has an externa ßeren circumference, distributed over the receiving areas for wing-like friction modules are arranged, wherein the friction assemblies are connected to the carrier element, wherein the Reibbau note each having a first friction lining and a second friction lining, wherein the first friction linings on the first friction lining carriers and the second Reibbe läge are arranged on second Reibbelagsträgem, and wherein further depending at least one Fe derelement between the first and the second friction lining carriers is arranged.
  • a friction lining in particular for metalli cal or metal-ceramic friction linings, of motor vehicle clutch discs consisting, inter alia, held in versions friction linings, which are arranged in pairs against each other on resilient lining carriers, with two identical lining carrier mutually, with their convex convex facing each other, are arranged, and each of the friction lining is connected with its version via at least two mounting rivets with its associated lining carrier and all mounting rivets of the twocominglie ing lining carrier are distributed over the existing area that against a Sym metrieline particular the pad carrier is a symmetrical distribution, without mutual overlap.
  • Each lining carrier has corresponding apertures in the region of the projection of the fastening rivets of the opposite lining carrier.
  • the versions of the friction linings also congruent with the Belagträgem perforations. Between the two Belagträgem on the line of symmetry at least one distance rivet for biasing the lining carrier is arranged.
  • a clutch disc for a friction clutch comprising a disc-shaped base body with a support member, wherein the Trä gerelement has an outer circumference, distributed over the receiving areas for wing-like friction assemblies are arranged, wherein the Reibbau phenomenon ment with the Suele are connected, wherein the friction assemblies each having a first friction lining and a second friction lining wx> are arranged on the first friction linings on first friction lining carriers, the first Reibbelags3.5 are connected to a spring element and the Fe derimplantation are connected to the carrier element, and wherein the second friction linings are arranged on second friction lining carriers, and wherein further the spring elements between the first and the second friction lining carriers are arranged.
  • the second friction lining carriers are connected directly to the carrier element.
  • the present invention has for its object to improve a clutch disc of the type mentioned, in particular to simplify their structure.
  • the object of the invention is ge in the above-mentioned clutch disc triggers that is arranged between the first and second friction lining carriers depending on a stop element, on which the spring elements are supported and / or in which the spring elements are partially received, and with the are connected to the first and second friction lining carrier or connected thereto, and further connected to the carrier element, further that the first friction lining are exclusively connected via a respective connecting element with the stop elements and that the spring elements are preferably formed as a plate springs.
  • the advantage here is that so that the structure of the friction assemblies can be structurally simplified. Along with this, the mass of the friction assemblies and thus the overall weight of the clutch disc can be reduced.
  • the reduction of the different individual parts of the friction assemblies can reduce the sources of error in the production process of the coupling slide.
  • Kings the attacks can be designed as a simple standard sheet metal elements.
  • the support of the first friction linings in the compressed state, ie in the coupled state of the clutch disc can be improved.
  • the usable friction volume of the friction linings can be increased, since a more uniform wear of the first friction linings is made possible by the improved contact of the first friction linings in the sprung state.
  • the spring elements as plate springs, the desired spring force can be more easily adapted to the respective application in comparison to spring plates.
  • the second friction pad are connected exclusively via a respective connecting element with the Antschele element and / or that between the second friction lining and the stop elements also spring elements, in particular plate springs , are arranged.
  • a simpler assembly and disassembly of the friction linings can be achieved if, according to a further embodiment of the clutch disc, the first and the second Reibbe- lagshav verbun via a common connecting element with the stop elements are the.
  • the clutch disc can be provided to who, that the connecting elements with which the first friction lining with the stop elements are connected to each extending through an opening in the spring elements, in particular cup springs, extend therethrough. It is thus a flexible, pivotable position tion and suspension of the first friction linings with the first friction lining on the Anschla gelementen reachable.
  • the compression can be improved when closing the clutch be, since a more even investment of the entire friction surface of the first friction linings can be achieved at the respective friction partners.
  • the spring elements in particular disc springs, which are arranged between the first Reibbelagsträgem and the stop elements, have a larger diameter than the Fe derimplantation, in particular disc springs arranged between the second friction lining carriers and the stop elements are. It can thus be achieved that the spring elements, in particular disc springs, are supported in different areas of the stop elements, whereby the drag losses of the clutch equipped with the clutch disc can be reduced. It can thus be the adhesion of the friction linings to fixed hitch be halves avoided with the clutch open.
  • the second friction pad are rigidly connected to the stop elements, so that therefore only the first friction linings are spring-mounted. It is in this way easily possible to provide a clutch disc with a resilient and a rigid side.
  • the first and the second Reibbe bearing carrier in the region of the connecting elements for the connection of the first and the two th friction lining with the stop elements have a recess for receiving the connecting elements.
  • Figure 1 is a clutch disc in a view in an oblique view from the front.
  • FIG. 2 shows a friction assembly of the clutch disk according to FIG. 1 in an exploded view and an oblique view
  • FIG. 3 shows a cross section through a wing-like friction assembly of the clutch disc of FIG. 1.
  • Fig. 5 cut a section of another embodiment of a clutch disc in side view
  • FIG. 6 shows a variant of a clutch disc in an oblique view from the front.
  • a first embodiment of a clutch plate 1 is shown for a known from the prior art friction clutch.
  • the clutch disc 1 substantially corresponds to those known in the art. Essentially, it is meant that - as will be explained in more detail below - differences in terms of the structure in relation to the frictional linings comprising Reibbau phenomenon exist.
  • the clutch disc 1 a in particular disk-shaped Grundkör by 2.
  • a plurality of torsion springs 3 are arranged on or in the main body 2 .
  • a recess 4 is centrally formed for receiving a shaft, not shown. Since this is known in principle from the prior art, reference is made to the relevant literature for details.
  • the base body 2 comprises a carrier element 5.
  • the carrier element 5 is arranged at least in the region of an outer circumference 6 of the base body 2.
  • the carrier element 5 extends over the entire base body 2, that is, from the recess 4 to the outer circumference 6.
  • the recess 4 is thus preferably (also) formed in the carrier element 5 from.
  • the torsion springs 3 are preferably arranged in corresponding receptacles in the carrier element 5.
  • the carrier element 5 can also be formed only ring element which is connected to the base body 2.
  • the carrier element 5 may also be formed integrally with the base body 2.
  • the carrier element 5 is made of a metal sheet, in particular a steel sheet.
  • the carrier element 5 is formed in one piece, that is not composed of several parts.
  • a plurality of receiving areas 7 arranged to receive wing-like friction assemblies 8 or formed.
  • a plurality of receiving areas 7 arranged to receive wing-like friction assemblies 8 or formed.
  • six receiving areas 7 and accordingly six friction assemblies 8 are present. However, this number should not be understood as limiting the invention. Rather, more or fewer receiving areas 7 and friction assemblies 8 may be present.
  • the friction assemblies 8 are verbun in the receiving areas 7 with the carrier element 5 to.
  • 8 holes are preferably provided both in the receiving areas 7 and the Reibbaugrup pen, so that each of the friction assemblies 8 surfaces with the dividendberei 7 via a plurality of rivets 9, which extend through these holes are connected.
  • the fixation i. the connection of the friction assemblies 8 with the receiving areas 7 of the carrier element 5 also takes place positively, for example by the receiving portion 7 facing end portion of the friction assembly 8, in particular a friction lining carrier, at least approximately 90 ° bent and inserted into a corresponding slot-shaped receptacle of the receiving area 7 is.
  • the positive connection can also be formed, for example, by a dovetail-shaped design of the end region of the friction assemblies 8, which engage in correspondingly shaped recesses in the receiving regions 7.
  • Each of the friction assemblies 8 of the clutch disc 1 forms its own assembly.
  • the friction assemblies 8 include or consist of, as is apparent from the exploded view in Fig. 2 and the cross section in Fig. 3, from a first friction lining 10, a second friction lining 11, a first friction lining support 12, a second friction lining support 13 and
  • two spring elements 14 are arranged, wherein a spring element 14 is assigned to the first Reibbelagscreme 12 and the second spring element 14 the second Reibbelagsträ ger 13.
  • Each friction assembly 8 has only one first friction lining 10 and only one second friction lining 11.
  • all friction assemblies 8 of the clutch disc 1 are identical.
  • the comments on the friction assembly 8 can therefore be transferred to all friction assemblies 8 of the clutch disc 1.
  • the first friction lining 10 is connected to the first friction lining carrier 12, preferably sintered on the sen.
  • connection methods can also be used.
  • the first friction lining 10 can be glued to the first friction lining carrier 12 or can be adhesively bonded thereto, for example soldered.
  • riveting or possibly screwing of the first friction lining 10 with the first friction lining carrier 12.
  • the same with regard to the connection methods applies to the second friction lining 11 and the second friction lining carrier 13 too.
  • the stop element 15 is in particular a sheet metal element, preferably made of a steel.
  • the stop element 15 has a plurality of openings 16 along an end face 16, via which the stop element 15 can be connected to the carrier element 5 in the manner described above, in particular riveted.
  • This end face 16 is preferably concavely curved, since it preferably the partial region of the circumference 6 of the Trä gerides 5 nachformt, in which the stop element 15 is arranged on the carrier element 5.
  • the stop element 15 has a spring element receptacle 17. This can be formed as a recess or as a break in the stop element 15.
  • the Federele ment recording 17 is preferably so large that the two spring elements 14 can be partially absorbed therein and optionally on the stop element 15 from support zen.
  • the Federele ment recording 17 has a diameter 18 which is greater than a (maximum) diameter 19 of the spring elements 14.
  • the size of the diameter 18 he spring element receptacle 17 is because preferably in such a dimensioned that the two Spring elements 14 just fit into this through broke 16 and that they can be easily installed (inserted).
  • the two spring elements 14 are formed in the preferred Ausdusangssection the clutch disc 1 as Telierfedem. They are in the passage 18 of the Anschlagele Mentes 15 gegentechnisch arranged such that they taper conically outwards in the direction of the first and second friction lining 12, 13, as can be seen from Fig. 2.
  • spring elements 14 can be used who the, for example, Evolutfedern, ring springs, etc.
  • spring elements 14 Kings which are arranged around the circumference of the aperture 18 extending around Kings NEN.
  • the versions can also be transferred to hitch be discs 1 with other spring elements 14.
  • the height of the spring elements 14 in the direction of the first friction lining support 12 and the second friction lining support 13 is preferably dimensioned so that they rest in any position on the spring elements 14, so both in the coupled and decoupled to stand.
  • Figs. 2 and 3 plate springs with circular shape (viewed in plan view) are provided, and this is also the preferred embodiment of the invention, Kings NEN also be shaped differently, such as square, etc.
  • the Federelementauf measure 17 adapted to the specific shape of the disc springs accordingly.
  • the friction assembly 8 no longer has any further spring elements.
  • the first and the second friction lining carrier 12, 13 have at the back, ie at the Anschlage gelement 15 facing surface, at least one driver element 20 (in the figures, only arranged on the first friction lining 12 driver elements 20 are visible bar), located in Direction of the stop element 15 and in this in one of the cross-sectional shape of the driver element 20 corresponding recess 21 or breakthrough extends.
  • the first and the second friction lining carrier 12, 13 depending Weil two driver elements 20. These are preferably arranged diagonally offset from one another. With the help of these driver elements 20 a rotation for the ers th and the second friction lining 10, 11 is achieved.
  • a height 22 of the driver 20 is dimensioned over the surface of the stop element 15 such that the Mit Converseele elements 20 engage in any relative position of the first and second friction lining carrier 12, 13 to the stop element 15 in the corresponding recesses 21 and openings.
  • a torque transmission can take place with the driver elements.
  • the driver elements 20 may be designed as bolts, which are connected to the first and the second friction lining carrier 12, 13. However, the driver elements 20 are preferably by deep drawing from the first and the second friction lining support 12, 13 Herge presents, so integrally formed with the first and the second friction lining 12, 13.
  • driver elements 20 shown it is also possible for more than the two driver elements 20 shown to be arranged or moved. be formed, for example, three, four, etc. Also in these embodiments, a diagonal arrangement as shown in Fig. 2, are selected, in which case (each) two driver elements 20 may be arranged side by side. Further, there is the possibility that all MitOSE he elements 20 are the same size, in particular special have an equal diameter. However, it is also different sized driver elements 20, in particular with different diameters, ver used. The smaller driver elements 20 may be radially further inside lie lowing and the larger driver elements 20 radially outward lying on the friction lining carriers 12, 13 may be arranged.
  • the first and the second friction lining carrier 12, 13 may each be separately connected directly to the stop element 15, for example via rivets, screws, etc.
  • the stop element 15 may be separately connected directly to the stop element 15, for example via rivets, screws, etc.
  • breakthroughs may be provided in the respective other friction lining and friction lining.
  • the preferred connection of the first and second friction lining carrier 12, 13 to the stop element 15 takes place according to embodiments of the clutch disc 1, however, by a common connecting element 23 which extends through the stop element 15 and the two disc springs.
  • the disc springs corresponding breakthroughs, as can be seen from Figs. 2 and 3.
  • the first and the second friction lining carrier 12, 13 are in this embodiment indirectly connected to the stop element 15 via the connecting element 23 (ie connected to the stop element 15) by the connecting element 23, the first and the second friction lining support 12, 13 interconnected and the Stop element 15 and the two disc springs is held by this connection between the first and the second friction lining carrier 12, 13, also with the help of the driver elements 20th
  • first and optionally the second friction lining carrier 12, 13 are connected in each case exclusively via a connecting element 23 to the stop element 15 in a direct or indirect manner. It can thus be formed together with the spring elements 14 is a "fulcrum" or pivotal mounting for the friction linings 10, 1 1, whereby they can be better brought to the respective friction partner to the plant.
  • the common connecting element 23 can be, for example, a one- or two-part rivet, or a screw with a nut, etc.
  • the first friction linings 12 and the second friction linings 13 are preferably made from a metallic or metal-ceramic sintered material customary for this purpose. However, it is also possible to produce these from other materials, such as resin-bonded fiber materials. These other types of friction linings are described in detail in the relevant literature, so reference is made to this point.
  • the first and second friction lining 12, 13 may be made of an iron-based material, for example, a steel, in particular a structural steel or a tempera tungsstahl. But it can also be brazing sheets, for example made of an iron-based material, in example of a steel, in particular a structural steel or a tempering steel, ver used.
  • the spring elements 16 may consist of a, in particular heat-resistant, spring steel.
  • the stop element 15 on the opening 16 for partially receiving the two plate springs can also be supported on an annular web, which is formed on a breakthrough 16 limiting side wall. It can also be provided that no breakthrough 16 but one or both sides only one recess is provided, in which the respective plate spring is partially received. It can further be provided that the Tel lerfedem are not partially received in a breakthrough or depression, son nes that the at least one plate spring on an outer surface 24, 25 of the Anschla guzes 15, in the direction of the respective friction lining 12, 13 shows, supports.
  • the arrangement of the disc springs shown in Figures 2 and 3 is the preferred because da with the disc springs in the assembled state of the friction assembly 8 are held in place and the opening 16 in the stop element 15 is easy to produce.
  • FIG. 4 shows a section through a friction assembly 8 of a variant of the clutch disc 1, wherein the plate spring, which is partially disposed between the first Reibbelagsträ ger 12 and the stopper member 15, has a larger diameter than the plate spring, partially between the second Reibbelagslic 13 and the Anschla gelement 15 is arranged.
  • the stop member 15 may have an annular web 26 on the side wall surrounding the opening 16, so that so these sides wall is formed with egg ner stage.
  • the diaphragm spring with the larger diameter is applied to the step on a surface adjacent to the end surface, while the smaller Tellerfe the aniiegt with its front side on the end face of the annular web 26, as shown in Fig. 4 Darge is.
  • Fig. 5 it is shown that it is possible, please include in a variant of the coupling slide 1, that a plate spring only the first friction lining support 12 (Fig. 2) is assigned.
  • the second friction lining carrier 13 is rigidly connected to the stop element 15, as shown in Fig. 5. This connection can be made, for example, by inverting the at least one driver element 20 or by means of a rivet, etc.
  • a further embodiment of the clutch disc 1 is shown, in which the first and the second friction lining 12, 13 in the region of the connecting element 23 for the connection of the first and the second friction lining carrier 12, 13 with the Anschlagele element 15 a recess 27 for Receiving the connecting element 20, ie a connec tion element head 28, have.
  • These depressions 27 are preferably as deep as corresponds to the height of the connecting element heads 28, so that in each case a connecting element head 28 is completely received in a recess 27, as shown in Fig. 4.
  • the stop element 15 has a raised portion which extends in the direction of the second friction lining carrier 13 or in the direction of the first friction lining carrier 12.
  • the raised area may be designed, for example, as a "ringwall" around the opening 16 in the stop element so as to limit the maximum possible travel, or in the region of attachment of the second friction bearing carrier 13 to the stop element 15
  • FIGS. 7 and 8 show the carrier element 5 and a friction lining carrier 12 for this clutch disk
  • the carrier element 5 is designed to extend outward in the area of the wing-like friction assemblies 8 and also forms the stop element 15 between the friction lining carriers 12, 13 (see also FIG. 2)
  • Carrier element 5 and the Ab tole elements 15 of the clutch disc 1 are thus made in one piece, as best seen in Fig. 7 can be seen.
  • the stop elements 15 are integrally formed in the carrier element 5.
  • the Trägement ement 5 for each friction assembly 8 a total of eight openings or recesses 21, which are each grouped around the central Federelementauf 17. These recesses 21 in turn serve to receive the participants with elements 20, each of which Reibbelagieri 12 has four, as seen in FIG 8 to see it.
  • the driver elements 20 are divided into two corner regions of the friction lining carrier 12. This pairwise division is not mandatory. It can also be arranged per Eckbe rich friction lining 12 each a driver element 20.
  • the driver elements 20 may be carried out deep-drawn or the thermoforming be backed with a bolt.
  • the clutch disc 1 is used in particular in a dry-running clutch, preferably in a dry-running clutch for a truck or a tractor.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un disque d'embrayage (1) pour un embrayage à friction pourvu de plusieurs ensembles de friction (8) en forme d'ailes agencés de manière à être répartis sur la circonférence, les ensembles de friction (8) comportant chacun une première garniture (10) de friction et une deuxième garniture (11) de friction, les premières garnitures (10) de friction étant agencées sur de premiers supports (12) de garnitures de friction et les deuxièmes garnitures (11) de friction sur de deuxièmes supports (13) de garnitures de friction, et au moins un élément de ressort (14) étant en outre agencé respectivement entre les premier et deuxième supports (12, 13) de garnitures de friction. Un élément de butée (15), contre lequel repose(nt) l'élément ou les éléments de ressorts (14) et/ou dans lequel il est/sont partiellement accueilli(s), et avec lequel les premier et deuxième supports (12, 13) de garnitures de friction sont raccordés ou auquel ceux-ci sont accolés, est agencé respectivement entre les premier et deuxième supports (12, 13) de garnitures de friction, les éléments de butée (15) étant en outre raccordés à un élément porteur (5). Les premiers supports (12) de garnitures de friction sont raccordés exclusivement à chaque fois par le biais d'un élément de raccordement (23) aux éléments de butée (15) et les éléments de ressorts (14) sont de préférence réalisés sous forme de ressorts à disques.
PCT/AT2019/060126 2018-04-16 2019-04-15 Disque d'embrayage Ceased WO2019200418A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201980025959.1A CN111989504B (zh) 2018-04-16 2019-04-15 离合器片
DE112019001963.5T DE112019001963A5 (de) 2018-04-16 2019-04-15 Kupplungsscheibe

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA50323/2018A AT521020B1 (de) 2018-04-16 2018-04-16 Kupplungsscheibe
ATA50323/2018 2018-04-16

Publications (1)

Publication Number Publication Date
WO2019200418A1 true WO2019200418A1 (fr) 2019-10-24

Family

ID=66655091

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/AT2019/060126 Ceased WO2019200418A1 (fr) 2018-04-16 2019-04-15 Disque d'embrayage

Country Status (4)

Country Link
CN (1) CN111989504B (fr)
AT (1) AT521020B1 (fr)
DE (1) DE112019001963A5 (fr)
WO (1) WO2019200418A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3108695A1 (fr) * 2020-03-31 2021-10-01 Valeo Embrayages Dispositif de progressivite pour disque d’embrayage a friction et disque d’embrayage a friction integrant un tel dispositif

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE678973C (de) * 1935-11-06 1939-07-26 Noel Banner Newton Kupplungsreibscheibe
DE7322146U (de) * 1973-09-13 Jurid Werke Gmbh Kupplungsscheibe mit sintermetallischen Reibbelagen
DE2920095A1 (de) 1979-05-18 1980-11-27 Fichtel & Sachs Ag Reibbelagbefestigung
DE19857712A1 (de) * 1997-12-18 1999-06-24 Luk Lamellen & Kupplungsbau Kupplungsscheibe
US20060231369A1 (en) * 2005-04-15 2006-10-19 Eaton Corporation Clutch disc assembly with direct bond ceramic friction material
WO2015024039A1 (fr) 2013-08-23 2015-02-26 Miba Frictec Gmbh Disque d'embrayage

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2093243A (en) * 1936-11-07 1937-09-14 Katcher Morris Friction clutch
GB499589A (en) * 1937-07-19 1939-01-19 Robert William Harvey Bailey Improvements in or relating to clutch plates
DE2036761C3 (de) * 1970-07-24 1973-09-13 Fichtel & Sachs Ag, 8720 Schweinfurt Kupplungsscheibe mit abgefederten metallischen oder metallkeramischen Reib belagen
US4869356A (en) * 1988-09-20 1989-09-26 Dana Corporation Clutch disk with spring cushioned friction element
DE19818871A1 (de) * 1998-04-28 1999-11-04 Mannesmann Sachs Ag Reibungskupplung mit Verschleißausgleich
CN202381574U (zh) * 2011-12-28 2012-08-15 浙江华信汽车零部件有限公司 铜基片、成对波形片分布的两级减振从动盘总成

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7322146U (de) * 1973-09-13 Jurid Werke Gmbh Kupplungsscheibe mit sintermetallischen Reibbelagen
DE678973C (de) * 1935-11-06 1939-07-26 Noel Banner Newton Kupplungsreibscheibe
DE2920095A1 (de) 1979-05-18 1980-11-27 Fichtel & Sachs Ag Reibbelagbefestigung
DE19857712A1 (de) * 1997-12-18 1999-06-24 Luk Lamellen & Kupplungsbau Kupplungsscheibe
US20060231369A1 (en) * 2005-04-15 2006-10-19 Eaton Corporation Clutch disc assembly with direct bond ceramic friction material
WO2015024039A1 (fr) 2013-08-23 2015-02-26 Miba Frictec Gmbh Disque d'embrayage

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3108695A1 (fr) * 2020-03-31 2021-10-01 Valeo Embrayages Dispositif de progressivite pour disque d’embrayage a friction et disque d’embrayage a friction integrant un tel dispositif

Also Published As

Publication number Publication date
CN111989504B (zh) 2022-03-01
AT521020A4 (de) 2019-10-15
CN111989504A (zh) 2020-11-24
DE112019001963A5 (de) 2020-12-24
AT521020B1 (de) 2019-10-15

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