WO2016038135A1 - Fixation d'une garniture de friction à une plaque support de plaquette de frein - Google Patents

Fixation d'une garniture de friction à une plaque support de plaquette de frein Download PDF

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Publication number
WO2016038135A1
WO2016038135A1 PCT/EP2015/070699 EP2015070699W WO2016038135A1 WO 2016038135 A1 WO2016038135 A1 WO 2016038135A1 EP 2015070699 W EP2015070699 W EP 2015070699W WO 2016038135 A1 WO2016038135 A1 WO 2016038135A1
Authority
WO
WIPO (PCT)
Prior art keywords
carrier plate
brake pad
bore
friction lining
brake
Prior art date
Application number
PCT/EP2015/070699
Other languages
German (de)
English (en)
Inventor
Matthias Niessner
Maik Schlauss
Gerrit Oswald
Werner Möhring
Original Assignee
Federal-Mogul Bremsbelag 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 Federal-Mogul Bremsbelag Gmbh filed Critical Federal-Mogul Bremsbelag Gmbh
Priority to EP15760201.2A priority Critical patent/EP3191730A1/fr
Publication of WO2016038135A1 publication Critical patent/WO2016038135A1/fr

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
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • 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
    • F16D69/00—Friction linings; Attachment thereof; Selection of coacting friction substances or surfaces
    • F16D69/04—Attachment of linings
    • 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
    • F16D69/00—Friction linings; Attachment thereof; Selection of coacting friction substances or surfaces
    • F16D69/04—Attachment of linings
    • F16D2069/0425—Attachment methods or devices
    • F16D2069/0433—Connecting elements not integral with the braking member, e.g. bolts, rivets

Definitions

  • the invention relates to a brake pad, in particular for a disc brake of a vehicle, with a carrier plate and at least one movably arranged on the carrier plate friction lining element.
  • the friction lining element is arranged on the carrier plate in such a way that, during braking operation, the friction lining element can be pressed against a brake disk by means of a first side face or is pressed against the brake disk.
  • Brake pads for disc brakes of vehicles usually have a support plate, for example made of steel, and arranged on the support plate friction lining.
  • the friction lining can be glued or pressed and otherwise connected to the carrier plate.
  • the connection between the support plate and the friction lining must withstand the forces occurring during braking operation, in particular the transverse forces and the forces resulting from vibration stresses.
  • Object of the present invention is to further improve a brake pad for a disc brake of a vehicle with a support plate and a movably arranged on the support plate Reibbelagelement that the load is reduced by the lateral forces occurring during braking on the carrier plate and the connection between the carrier plate and friction lining and thus the brake pad has a long service life even with impact loads.
  • a brake pad in particular for a disc brake of a vehicle, is proposed for this purpose, the brake pad having a carrier plate and at least one friction lining element movably arranged on the carrier plate.
  • the friction lining element is arranged on the carrier plate in such a way that during brake actuation the friction lining element a brake disc is pressed. In this case, the friction lining element is pressed against a brake disk with a first side surface of the friction lining element.
  • the carrier plate For attachment of the friction lining element with the carrier plate, the carrier plate has a through hole. In the bore, a fastening means for connecting the friction lining element is arranged with the carrier plate.
  • the attachment means may be connected to a sleeve disposed in the bore. Alternatively or additionally, the attachment means may be secured within the bore by means of an elastic closure means for axially securing the position of the attachment means.
  • the friction lining element can have different shapes or geometries.
  • a first side surface of the friction lining element is directed towards the brake disk of a brake, or is the brake disk facing side.
  • the second side surface of the friction lining element faces the carrier plate.
  • the friction lining element preferably also has a bore.
  • the bore is used by the friction lining member receiving the fastening means, for example a screw or a bolt, for connecting the friction lining element to the carrier plate.
  • the friction lining element is preferably arranged on the carrier plate such that the bore through the carrier plate and the bore through the friction lining element are arranged corresponding to one another.
  • the two holes can have different diameters.
  • the fastener is passed through the bore in the friction lining member and inserted and secured in the bore or bushing disposed in the bore.
  • the Reibbelagelennent is movable to the support plate, or relatively movable to the support plate, is arranged.
  • the Reibbelagelennent is perpendicular, or in the axial direction, arranged to the support plate movable.
  • the friction lining element can be arranged on the carrier plate such that the friction lining element is pivotable about an axis arranged substantially parallel to the carrier plate.
  • this axis has an intersection with a center axis directed perpendicular to the carrier plate through the bore in the carrier plate.
  • a socket for receiving the fastener such as the screw or bolt is provided and, for example, not a screw is screwed directly without a socket in the bore through the support plate, the lateral force is when the brake is actuated discharged via the friction lining element to the socket.
  • the load on the carrier plate is reduced in this area.
  • the fastening means is secured by means of an elastic closure means for securing the axial position of the fastening means within the bore.
  • the friction lining element is guided in the vertical direction or in the axial direction by such an attachment. Furthermore, these fasteners allow easy mounting.
  • the fastening means may preferably be designed as a screw.
  • the friction lining is then by means of a screw with the in the Bore connected through the support plate arranged bushing.
  • the screw has an external thread and the socket at least partially an internal thread.
  • the internal thread over the entire length of the socket as well as only partially be provided.
  • the fastening means is designed as a bolt or bolt-shaped, wherein the fastening means comprises a head part and an adjoining pin.
  • the headboard may be round or angular, for example hexagonal.
  • the pin preferably has a circular cross-section, wherein the diameter of the pin at each point is smaller than the diameter or the maximum width of the head part.
  • the pin may have a substantially constant diameter or be conical. By a substantially constant diameter is meant that the diameter is constant over at least three quarters of the length of the pin.
  • the elastic closure means is an integral part of the fastening means or is formed as a separate component.
  • the bolt in particular the pin of the bolt, may be partially formed as an elastic closure member and thus be the elastic closure means an integral part of the fastening means.
  • the elastic closure means could be annular and circumferentially disposed around the pin.
  • the ring-shaped trained elastic closure means may be formed as an open or flexible closed ring.
  • the pin of the bolt-shaped fastening means is preferably sleeve-shaped and at least partially hollow. Furthermore, a front end of the pin is preferably designed to be open.
  • the elastic closure part comprises a spring means, in particular a bending spring, which is formed by substantially longitudinally directed slots in a wall of the pin.
  • the longitudinal slot is preferably arranged from the open front end of the bolt or the pin towards the head part over a length of at least half the length of the pin in the wall of the pin.
  • the spring means is tab-shaped, wherein the tab is connected only at one end to the wall of the pin or formed integrally with this wall of the pin.
  • the preferred spring means on three freestanding or not connected to the wall of the pin edges.
  • the spring means acts as a snap closure after pressing the bolt into the bore or arranged in the bore socket.
  • the elastic closure means comprises a plurality of spring means formed in the wall of the pin, in particular a plurality of bending springs, which are distributed circumferentially and separated from one another by at least three longitudinally directed slots.
  • the slots arranged in the wall of the pin are arranged in particular in the region in which the pin is hollow in the interior.
  • the slots are formed in this area as complete openings through the wall of the pin.
  • At least four spring means separated by four longitudinal slots are provided. Furthermore, it is preferably provided that the plurality of spring means of the elastic closure means are arranged circumferentially evenly distributed and have substantially equal widths. As a result, a circumferentially uniformly distributed snap effect can be achieved when the fastening means are pressed into the bore or the bushing arranged in the bore.
  • a protruding outward elevation is arranged or a wall of the pin has in regions a thickening.
  • the survey or the thickening engages in a recess in an inner wall of the bore or in a recess of a bush arranged in the bore.
  • the survey or the thickening is preferably arranged at the front end of the pin.
  • the elevation or thickening is preferably formed as a circumferential bead, edge or as a circumferential ring, wherein the elevation or the thickened area may be partially interrupted by the slots arranged in the wall of the pin.
  • the recess in the inner wall of the bore or the inner wall of the bushing may be formed as a groove or as a recess.
  • the bolt is preferably secured by means of a securing means, in particular a safety sleeve, within the bore or within the socket.
  • a securing means in particular a safety sleeve
  • the securing means for example the securing sleeve
  • a transition or interference fit is preferably provided to secure the securing means against migration out of the fastening means.
  • the brake pad is fully adjacent to a pad holder, whereby a displacement of the securing means is prevented.
  • the securing means for example the securing sleeve, particularly preferably has an inner container as a dismantling aid.
  • the elastic closure means may be preferably annular, in particular as a securing ring, be formed and disposed in a wall of the pin groove arranged around the pin around.
  • a circlip for example, a Nutenring or Seeger ring to understand.
  • a circlip according to the present invention is an axial position assurance machine member of the fastener, such as the bolt, in the bore or bushing disposed in the bore.
  • the securing ring can also be designed as a lamellar ring.
  • the retaining ring acts as a spring ring, which is yielding in the radial direction.
  • the circlip is before mounting the fastener, such as the bolt, preferably radially or axially on the bolt, or the pin of the bolt, pushed and into the circumferentially outwardly disposed in the wall of the pin groove.
  • the wire ends of the annular opening of the securing ring are preferably arranged extending in the radial direction from the center of the ring to the outside.
  • the length of the sleeve disposed in the bore through the support plate is greater than the depth of the bore.
  • the bushing has a greater length compared to the thickness of the carrier plate in this area.
  • the bush preferably projects out of the bore through the carrier plate in such a way that the bushing projects at least partially into the bore through the friction lining element with the end projecting out of the bore.
  • the bush is preferably at least partially, that is, at least one end disposed within the bore through the friction lining.
  • the sleeve protrudes over a predetermined length from the bore through the support plate.
  • the length of the bush is at least 20%, more preferably at least 30%, and most particularly preferably at least 40%, greater than the depth of the bore through the support plate.
  • an outwardly projecting flange is preferably formed.
  • the outwardly projecting flange is formed such that thereby a stopper is formed relative to the carrier plate.
  • the flange is preferably fully disposed around the sleeve at the first end of the sleeve.
  • the flange is integrally formed projecting outwardly, the flange of the outer wall of the socket, preferably in the radial direction, from.
  • the flange is arranged substantially perpendicular to the outer wall of the socket.
  • the flange has a contact surface, which comes to bear against the carrier plate to form the stop relative to the carrier plate.
  • This contact surface is preferably arranged substantially parallel to a friction lining element facing side surface of the support plate.
  • the bushing or the flange projecting outwardly at a first end of the bush forms a stop relative to the carrier plate.
  • the second end, namely the end projecting into the bore through the friction lining element, the bushing is designed such that the bushing in this area forms a stop relative to the fastening means, for example the screw.
  • the facing away from the friction lining element side surface of the support plate is referred to in the present as the first side surface of the support plate.
  • the friction lining facing side surface of the carrier plate is referred to as the second side surface of the carrier plate.
  • the support plate in the region of the bore through the support plate on the first Side surface of the support plate on a depression.
  • the recess is preferably substantially around the bore, and quite preferably circumferentially completely around the bore, arranged.
  • the recess may have a round, oval or angular shape.
  • the recess has a round shape and thus a diameter.
  • the maximum width of the recess is preferably larger than the diameter of the bore through the carrier plate. It is preferably provided that the maximum width is at least 10%, more preferably at least 15%, and most preferably at least 20% greater than the diameter of the bore through the support plate. With a round depression, the diameter of this depression corresponds to the maximum width of the depression.
  • the bush is arranged in the bore through the support plate, that the flange is at least partially disposed within the recess.
  • the flange is arranged completely in the recess.
  • the flange or the sleeve does not protrude beyond the first side surface of the support plate from the bore through the support plate.
  • a protrusion is preferably arranged in the carrier plate on the second side surface of the carrier plate.
  • the survey is integrally formed with the carrier plate.
  • the survey for example, as a connected to the support plate element, for example be designed as a welded ring.
  • the support plate may be formed with elevation and depression as a casting.
  • the recess and the survey are formed by forming the support plate.
  • a spring element is preferably arranged between the carrier plate and the friction lining element.
  • the spring element serves for the movable arrangement of the friction lining element on the carrier plate.
  • the spring element is circumferentially arranged around the bore through the carrier plate on the second side surface of the carrier plate.
  • the sleeve preferably protrudes with one end into the bore through the friction lining element, when screwing in the fastening means, such as the screw, a defined bias of the movable connection between the carrier plate and the friction lining element can be produced.
  • the screw is screwed into the socket until the screw head forms a stop relative to one end of the socket.
  • the spring element is tensioned or prestressed between the friction lining element and the carrier plate is arranged.
  • the spring element preferably has an opening for the passage of the fastening means, for example the screw. By means of the screw connection, the friction lining element is pressed against the spring element. With the other side, the spring element is pressed against the carrier plate.
  • the spring element is preferably arranged around the survey around.
  • the survey can serve to guide or fix the spring element.
  • To guide or fix the spring element is thus no additional attachment, such as welded disc, necessary.
  • the spring element is designed as a plate spring.
  • the plate spring is arranged such that the bottom portion rests against the second side surface of the carrier plate and has an opening or through bore for the passage of the fastening means, for example the screw. The resilient edge of the plate spring is pressed against the second side surface of the friction lining element.
  • the friction lining element can have any suitable shape or geometry.
  • the basic shape of the friction lining element has a substantially round, oval, triangular, square, rectangular or trapezoidal shape. This is to be understood that only the basic form is formed in this way. For example, the corners may be rounded, but this does not change the basic shape. Thus, for example, it is provided that the friction lining element in the Has substantially triangular or trapezoidal basic shape with rounded corners.
  • the brake lining On the second side surface of the support plate a plurality of friction lining elements can be arranged. It is particularly preferably provided that more than three, more preferably more than four, friction lining elements are arranged on the second side surface of the support plate. In the arrangement of a plurality of friction lining elements on the second side surface of the carrier plate, the friction lining elements are also referred to as Reibbelagsegmente.
  • the brake lining preferably has a segmented friction lining, wherein the individual segments are formed by the friction lining elements.
  • a disc brake for a vehicle in particular a rail vehicle, is further provided, wherein the disc brake has a brake pad according to claims 1 to 24.
  • FIG. 1 is a perspective view of a brake pad
  • FIG. 3 shows a sectional view through a region of a brake pad
  • 5a is a perspective view of a fastener
  • 5b to 5d are sectional views of a fastening means, a socket and a securing means
  • Fig. 6 is a sectional view through a portion of a friction lining
  • FIG. 7a to 7c are sectional views of a fastener, an elastic closure means and a socket. Preferred embodiments of the invention
  • FIG. 1 shows a perspective view of a brake pad 100.
  • the carrier plate 10 of the brake pad 100 has on the first side face 28 a guide plate 33 for attachment or attachment of the brake lining 100 in a disc brake 200.
  • the disc brake 200 is not shown in FIG.
  • On the second side surface 29 of the support plate 10 five friction lining elements 11 are arranged.
  • the friction lining elements 11 have a substantially triangular basic shape with rounded corners.
  • friction lining elements 11 are arranged movable to the support plate 10. When braking, the friction lining elements 11 are pressed with a first side surface 12 to a brake disc (not shown in Figure 1) of a brake.
  • the friction lining elements 11 are connected to the carrier plate 10 by means of a fastening means.
  • the support plate 10 each have a bore 14 for each friction lining element 11.
  • a bush 15 is pressed with internal thread 18.
  • Each friction lining element 11 has a bore 16 through which the fastening means is passed in order to connect the friction lining element 11 with the bush 15.
  • FIG. 2 shows a cross section through a brake pad 100.
  • the carrier plate 10 has a first side surface 28 around the bore 14 Recess 24 on.
  • the recess 24 was produced by a forming process or by impressing the carrier plate 10.
  • the support plate 10 may be formed with recess 24 and elevation 25 as a casting.
  • a spring element 32 Around the elevation 25 around a spring element 32 is arranged in the form of a plate spring.
  • the elevation 25 thus serves to guide or fix the spring element 32.
  • a spring element 32 between the support plate 10 and the friction lining 11 a movable arrangement of the friction lining element 11 to the support plate 10 is possible.
  • a bushing 15 In the bore 14 through the support plate 10, a bushing 15 is arranged.
  • the bush 15 has an internal thread 18 for receiving a screw 17. By means of the screw 17, the friction lining element 11 is screwed to the bush 15.
  • the bush 15 has at a first end 20 an outwardly projecting flange 22.
  • the bush 15 is arranged in the bore 14 through the support plate 10 such that the flange 22 is disposed completely in the recess 24.
  • the bushing 15 does not protrude beyond the first side surface 28 of the carrier plate 10.
  • the bushing 15 protrudes with its second end 21 out of the bore 14 through the carrier plate 10 and protrudes at least partially into the bore 16 through the friction lining element 11.
  • FIG. 3 shows a section of the brake lining 100 in a cross-sectional view.
  • the area of the bore 14 is through the carrier plate 10 and the bore 16 through the friction lining member 11 and arranged in the bore 14 through the support plate 10 socket 15 is shown.
  • the bore 14 through the support plate 10 has a diameter 26.
  • the diameter 26 substantially corresponds to the outer diameter of the bushing 15.
  • the bushing 15 is pressed into the bore 14 through the support plate 10.
  • the outwardly projecting flange 22 of the bushing 15 is completely disposed in the recess 24 of the support plate 10 on the first side surface 28.
  • the arranged opposite the recess 24 elevation 25 of the support plate 10 serves as a fixation and guidance for the spring element 32.
  • the spring element 32 is arranged in the form of a plate spring around this elevation 25 on the second side surface 29 of the support plate 10. The resilient edge of this plate spring is pressed or pressed against the second side surface 29 of the friction lining element 11.
  • the friction lining element 11 is connected to the carrier plate 10.
  • the screw 17 is screwed into the socket 15.
  • a desired bias of the spring element 32 can be specified.
  • the screw 17 is screwed into the socket 15 until the screw 17 forms with its head a bearing relative to the second end 21 of the socket.
  • the length 19 of the bushing 15 is selected as short as possible. At a greater length 19 of the bushing 15, the bias of the spring element 32 is reduced.
  • the maximum width 27 of the recess 24 is greater than the diameter 26 of the bore 14 through the support plate 10. Furthermore, the maximum width is 27 the recess 24 larger than the outer diameter of the bushing 15 in the region of the outwardly projecting flange 22nd
  • FIG. 4 shows a further sectional view through a region of a brake pad 100.
  • the same region of the brake lining 100 is shown as in FIG. 3.
  • the fastening means 40 is not designed as a screw but as a bolt 42.
  • the bolt 42 has a head part 43 and an adjoining substantially cylindrical pin 44.
  • the wall 47 of the pin 44 is formed thickened or has on the outer surface of a survey 49 or thickening 50 on.
  • the bolt 42 is hollow in the region of the pin 44 and has longitudinally arranged in the wall 47 of the pin 44 slots 46. Through these slots 46 spring means 48 are formed in the form of bending springs or spring tabs.
  • the bolt 42 is pressed through the bore 16 through the friction lining 11 in the arranged in the bore 14 through the support plate 10 bushing 15, wherein he presses in with the thickened portions at the front end 45 of the pin 44 in an annularly arranged recess 51 on the Inner wall 53 of the bush 15 engages.
  • FIG. 5a shows a perspective view of a bolt 42 with a head part 43 and pins 44 protruding therefrom or adjoining it.
  • the wall 47 of the pin 44 has longitudinally directed slots 46, whereby spring means 48 are formed in the form of flexible springs or spring tabs ,
  • Fig. 5c shows a sectional view of a bushing 15 as it is inserted into the bore 14 through the support plate 10 of FIG.
  • 5d shows a sectional view through a securing means 54 which serves to secure the bolt 42 inserted into the bushing 15.
  • the securing means 54 can be pressed into the opening of the bolt 42 from below after insertion of the bolt 42. To secure the securing means 54 against wandering out of the opening, a transition or slight interference fit is sufficient. As a disassembly aid, the securing means 54 is formed with an internal thread.
  • Fig. 6 shows a further sectional view through a portion of a brake pad as shown in FIGS. 3 and 4.
  • the fastening means 40 is formed as a bolt 42, wherein the elastic closure means 41 is not an integral part of the bolt 42 is.
  • the elastic closure means is designed as a securing ring and inserted into a groove 55 on the outer surface of the bolt 42.
  • the retaining ring acts as a spring ring and is yielding in the radial direction.
  • FIG. 7b shows a sectional representation of a securing ring as elastic closure means 51. So that the circlip before mounting the Bolzens 42 can be pushed radially onto the bolt 42, the locking ring is formed such that the wire ends in the ring opening in the radial direction from the center of the ring to the outside.
  • FIG. 7a and 7c show sectional views of a bolt 42 and a bushing 15 as they are inserted into the bore 14 through the support plate 10 in the embodiment shown in Fig. 6.

Abstract

Plaquette de frein (100) pour frein à disque de véhicule, comprenant une plaque support (10) et un élément garniture de friction (11) monté mobile sur la plaque support, l'élément garniture de friction étant destiné à être fixé à la plaque support (10) par un moyen de fixation (40) disposé dans un orifice ménagé dans la plaque support, et le moyen de fixation devant être relié à une douille (15) ou être fixé dans l'orifice par un moyen de fermeture élastique aux fins de blocage en position axiale du moyen de fixation (40).
PCT/EP2015/070699 2014-09-10 2015-09-10 Fixation d'une garniture de friction à une plaque support de plaquette de frein WO2016038135A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP15760201.2A EP3191730A1 (fr) 2014-09-10 2015-09-10 Fixation d'une garniture de friction à une plaque support de plaquette de frein

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014113058.8 2014-09-10
DE102014113058.8A DE102014113058A1 (de) 2014-09-10 2014-09-10 Verbindung eines Reibbelages auf einer Trägerplatte eines Bremsbelages

Publications (1)

Publication Number Publication Date
WO2016038135A1 true WO2016038135A1 (fr) 2016-03-17

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ID=54065377

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Application Number Title Priority Date Filing Date
PCT/EP2015/070699 WO2016038135A1 (fr) 2014-09-10 2015-09-10 Fixation d'une garniture de friction à une plaque support de plaquette de frein

Country Status (3)

Country Link
EP (1) EP3191730A1 (fr)
DE (1) DE102014113058A1 (fr)
WO (1) WO2016038135A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202016103354U1 (de) 2016-06-24 2016-08-19 Faiveley Transport Witten Gmbh Bremsbelag
CN107061576A (zh) * 2017-03-09 2017-08-18 湖南博科瑞新材料有限责任公司 一种动车组用的粉末冶金闸片

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020115398A1 (de) 2020-06-10 2021-12-16 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Bremsbelag für eine Scheibenbremse eines Fahrzeugs und Scheibenbremse
DE102020120170B3 (de) * 2020-07-30 2021-06-17 DISK Friction Materials Europe GmbH Scheibenbremsbelag für gleisgebundene Fahrzeuge

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DE2363427A1 (de) * 1973-12-20 1975-06-26 Licentia Gmbh Reibscheibe fuer kupplungen oder bremsen
GB2205133A (en) * 1987-05-29 1988-11-30 Fichtel & Sachs Ag Clutch disc for a friction disc clutch
DE20205315U1 (de) * 2002-03-21 2002-07-25 Becorit Gmbh Bremsbelag für eine Scheibenbremse und Reibelement

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AT48568B (de) * 1910-10-26 1911-06-26 Wilhelm Walter Druckknopf mit mehrfacher Klemmung.
US1789133A (en) * 1928-10-18 1931-01-13 Ferodo Sa Method for securing friction facing members
US4076106A (en) * 1976-10-19 1978-02-28 Goodyear Aerospace Corporation Snap fasteners for brake disk wear plates
IT1261780B (it) * 1993-04-05 1996-06-03 Pattino per freni a disco con elementi di attrito sinterizzati.
DE10215170B4 (de) * 2002-03-21 2005-02-24 Becorit Gmbh Bremsbelag für eine Scheibenbremse und Reibelement
JP5706237B2 (ja) * 2011-06-02 2015-04-22 新日鐵住金株式会社 鉄道車両用ブレーキライニングおよびそれを備えたディスクブレーキ

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2363427A1 (de) * 1973-12-20 1975-06-26 Licentia Gmbh Reibscheibe fuer kupplungen oder bremsen
GB2205133A (en) * 1987-05-29 1988-11-30 Fichtel & Sachs Ag Clutch disc for a friction disc clutch
DE20205315U1 (de) * 2002-03-21 2002-07-25 Becorit Gmbh Bremsbelag für eine Scheibenbremse und Reibelement

Non-Patent Citations (1)

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Title
See also references of EP3191730A1 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202016103354U1 (de) 2016-06-24 2016-08-19 Faiveley Transport Witten Gmbh Bremsbelag
WO2018002472A1 (fr) 2016-06-24 2018-01-04 Flertex Sinter Ensemble de plaquettes de frein
CN107061576A (zh) * 2017-03-09 2017-08-18 湖南博科瑞新材料有限责任公司 一种动车组用的粉末冶金闸片

Also Published As

Publication number Publication date
EP3191730A1 (fr) 2017-07-19
DE102014113058A1 (de) 2016-03-10

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