EP3877669A1 - Support de garniture de frein pour un véhicule ferroviaire - Google Patents

Support de garniture de frein pour un véhicule ferroviaire

Info

Publication number
EP3877669A1
EP3877669A1 EP19795473.8A EP19795473A EP3877669A1 EP 3877669 A1 EP3877669 A1 EP 3877669A1 EP 19795473 A EP19795473 A EP 19795473A EP 3877669 A1 EP3877669 A1 EP 3877669A1
Authority
EP
European Patent Office
Prior art keywords
brake
pad holder
spring
base body
brake pad
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP19795473.8A
Other languages
German (de)
English (en)
Inventor
Ferenc Müllek
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.)
Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
Original Assignee
Knorr Bremse Systeme fuer Schienenfahrzeuge 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 Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH filed Critical Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
Publication of EP3877669A1 publication Critical patent/EP3877669A1/fr
Withdrawn legal-status Critical Current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
    • F16D69/00—Friction linings; Attachment thereof; Selection of coacting friction substances or surfaces
    • F16D69/04—Attachment of linings
    • F16D69/0408—Attachment of linings specially adapted for plane linings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61H—BRAKES OR OTHER RETARDING DEVICES SPECIALLY ADAPTED FOR RAIL VEHICLES; ARRANGEMENT OR DISPOSITION THEREOF IN RAIL VEHICLES
    • B61H5/00—Applications or arrangements of brakes with substantially radial braking surfaces pressed together in axial direction, 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
    • F16D2069/0425—Attachment methods or devices
    • F16D2069/0433—Connecting elements not integral with the braking member, e.g. bolts, rivets
    • 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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/2245—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members in which the common actuating member acts on two levers carrying the braking members, e.g. tong-type 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
    • F16D65/00—Parts or details
    • F16D65/0006—Noise or vibration control

Definitions

  • the present invention relates to a brake pad holder for a disc brake of a rail vehicle according to the preamble of claim 1.
  • Brake linings for disc brakes of rail vehicles as are known for example from DE 10 2009 006 290 A1, have a guide web provided on the back of the brake lining, which is held in a guide channel of a pressure plate of a lining holder.
  • the guide channel and correspondingly the guide web extend in the longitudinal direction of the pad holder.
  • brake pads it is also known to design the brake pads in two parts and to lock two brake pad halves one behind the other to the pad holder.
  • the brake pad halves are also referred to below as brake pads for the sake of simplicity.
  • the guide channel and correspondingly the guide web of the respective brake lining are preferably dovetail-shaped in cross section.
  • Another disadvantage of a gradually increasing play between the guide channel and the guide web is that in the case of a dovetail-shaped guide, the brake pads are kept at a greater distance from the pressure plate of the pad holder, since the dovetail-shaped guide webs and the corresponding dovetail-shaped guide channel in the advanced state of wear also has increased play in a direction perpendicular to the surface of the pressure plate.
  • the object of the present invention is to provide a brake pad holder for a disc brake of a rail vehicle, with which the above problems can be largely avoided and with which, in particular, a less wear-prone coupling between the brake pads and the pad holder is made possible.
  • the brake pad holder according to the invention for a rail vehicle has a pad holder and at least two brake pads held on the pad holder.
  • the pad holder has a pressure plate with a guide channel extending in the longitudinal direction of the pad holder, in which a guide bar arranged on a rear side of the brake pads facing the pressure plate is slidably held.
  • the guide web of the brake pads has a receiving channel that extends in the direction of displacement and in which a spring rod is received.
  • the spring bar has a plurality of spring elements which are arranged such that, when the spring bar is inserted into the receiving channel, a torque acts on the brake pads perpendicular to the direction of displacement.
  • the guide webs are rotated by a small angle in the guide channel about an axis of rotation oriented perpendicular to the pressure plate, and thereby parts of the side surfaces against the inner surfaces of the guide channel pressed, which leads to an elimination of the play required for assembly between the guide webs and the guide channel in the fully assembled state.
  • Eliminating this play with the spring rod inserted in the receiving channel creates a friction between the guide webs and the guide channel, which means that no relative movement between the guide channel and the guide webs takes place in ferry operation in a non-braking position, and thus the wear is significantly reduced.
  • the spring rod has a rod-shaped base body on which the spring elements are arranged on opposite longitudinal sides.
  • the base body has, in particular, a polygonal, in particular cuboid cross-section, which facilitates the assembly or molding of spring elements on flat surfaces.
  • a rod-shaped base body with a circular cross section is also conceivable.
  • the spring elements are on
  • Base body attached, in particular riveted, screwed or locked. This enables simple replacement of individual spring elements in the event of damage to one of the spring elements.
  • the spring elements are designed as leaf springs or spring-loaded rollers.
  • leaf springs or spring-loaded rollers can be produced reliably and stably and inexpensively during operation.
  • the spring elements are arranged alternately on opposite longitudinal sides of the base body of the spring rod, so that two spring elements each rest on each receiving channel of the brake pads.
  • respective spring elements are arranged in the area of the ends of the base body of the spring bar on the same long side of the base body of the spring bar and in the center area of the base body of the spring bar two spring elements are arranged on the opposite long side of the base body of the spring bar.
  • a tool holder is formed at least in a region of the rear end of the base body in the direction of insertion.
  • the tool holder can be designed, for example, in the form of a bayonet lock, so that the spring rod can be pulled out of the holder channel of the brake pads in a simple manner after insertion into the tool holder, which results in the slight twisting of the guide webs or the brake pads in the guide channel picks up and the brake pads can thus be detached from the pad holder in a simple manner.
  • a partial area adjacent to a peripheral edge of at least one of the brake pads of an end face facing a second one of the brake pads is angled by an angle of less than 2 ° with respect to the remaining end face of the brake pad.
  • the width of the angled partial area of the end face perpendicular to the direction of displacement is less than 20% of the total width of the brake pad.
  • Fig. 1 is a perspective view of a pad holder
  • FIG. 2 shows a perspective illustration of the brake linings with a representation of guide webs arranged on the brake linings and a receiving channel introduced into the guide web
  • 3 shows a perspective illustration of an embodiment variant of a spring bar
  • FIG. 4 is an exploded perspective view of the spring bar shown in FIG. 3,
  • FIG. 5 shows a sectional view through the brake pad holder shown in FIG. 1 to illustrate the interaction between the guide channel, guide web and spring rod,
  • FIG. 6 shows a sectional illustration through a plane parallel to the pressure plate on the flea of the guide channel and the guide web
  • FIG. 7 is a plan view of the brake pads of FIG. 2,
  • FIG. 8 is a plan view of a spring bar with mutually arranged spring elements
  • Fig. 9 is a schematic plan view of a spring bar with an alternative arrangement of the spring elements.
  • top, bottom, left, right, front, rear, etc. refer exclusively to the exemplary representation and position of the pad holder, pressure plate, brake pad, guide channel, guide bar, spring bar and the like selected in the respective figures. same. These terms are not to be understood as restrictive, i.e. these references can change due to different working positions or the mirror-symmetrical design or the like.
  • FIG. 1 shows an embodiment variant of a brake pad holder according to the invention for a rail vehicle.
  • the brake pad holder has a pad holder 2 known per se from the prior art, with a brake lever bearing 24 for mounting a brake lever, a pressure plate 21, on the brake lever bearing 24, on which a guide channel 22 extending in the longitudinal direction of the pad holder 2 is formed.
  • Guide webs 32a, 32b are held displaceably in this guide channel 22 by two brake pads 3a, 3b.
  • the two brake pads 3a, 3b are shaped here in such a way that they could also be referred to as brake pad halves of a brake pad 3. It would also be conceivable here to arrange three or more brake pad parts in succession in the guide channel 22 instead of two brake pad halves or to divide a two-part brake pad not in the middle, but into a larger section, that is to say a longer one in the direction of displacement x and a smaller section, that is to say a shorter one in the direction of displacement x . Therefore, the “two-part brake pads” shown in the exemplary embodiments, consisting of two brake pad halves, are referred to below generally as brake pads.
  • the guide webs 32 are arranged on the rear side 31a, 31b of the brake pads 3a, 3b facing the pressure plate 21.
  • the guide webs 32 are preferably formed from the friction lining material of the brake lining 3 on the rear side of the respective brake lining 3a, 3b facing away from the friction surface.
  • the guide webs 32 are encased by a carrier plate 4, which serves to reinforce the guide web 32.
  • the guide web 32 and correspondingly the guide channel 22 are dovetail-shaped, the width of the guide web 32 to the pressure plate 21 increasing in a direction z perpendicular to the friction surface of the brake pads 3a, 3b .
  • the guide web 32 has a receiving channel 5 which extends in the displacement direction x and in which a spring rod 6 is received.
  • the spring bar 6 has a plurality of spring elements 62 which are arranged such that, when the spring bar 6 is inserted in the receiving channel 5, a torque perpendicular to the direction of displacement x on the brake pads 3a, 3b acts.
  • the spring rod 6 has a rod-shaped base body 61.
  • the spring elements 62 are arranged on opposite longitudinal sides of the rod-shaped base body 61.
  • the spring elements 62 are fixed to the base body 61 with rivets 64.
  • the spring elements 62 are preferably designed as leaf springs, as shown in FIGS. 3 and 4. Other configurations of spring elements such as spring-loaded rollers are also conceivable.
  • the receiving channel 5 is preferably U-shaped, as is shown by way of example in FIG. 5.
  • the width of the guide web 32a, 32b is slightly smaller than the width of the guide channel 22 in the pad holder 2, so that for installing the brake pads 3a, 3b, in which the brake pad 3b is first used its guide bar 32 is inserted into the guide channel 22 in the pressure plate 21 of the pad holder 2, then the second brake pad 3a is inserted with its guide bar 32 into the guide channel 22, the guide bars 32 of the brake pads 3a, 3b are inserted or inserted in a simple manner can.
  • the spring bar 6 is subsequently connected the receiving channel 5 inserted here in the middle of the guide webs.
  • the two brake pads 3a, 3b are coupled to one another in such a way that a torque acts on the brake pads 3a, 3b via the spring bar 6.
  • This torque leads to the brake pads 3a, 3b being rotated slightly about an axis of rotation extending in the z-direction, and the guide webs 32 thereby partially, in particular in line form, bear against the guide channel 22 with friction, which means that under normal driving conditions in the non-braking state, the brake pads 3a, 3b do not move back and forth relative to the guide channel 22.
  • the minimal rotation of the brake pads 3a, 3b within the guide channel 22 can be achieved by different arrangements of the spring elements 62 on the base body 61 of the spring rod 6.
  • the spring bar 6 shown in FIGS. 3 and 4 has a total of four such spring elements 62.
  • a configuration with, for example, six or eight spring elements would also be conceivable, provided that not only two brake pads, but, as explained above, three or four brake pads were inserted one after the other into the guide channel 22 of the pad holder 2. It is important that the spring elements are arranged in such a way that a torque is exerted on each of the brake pads 3a, 3b.
  • respective spring elements 62 are arranged in the region of the ends of the base body 61 of the spring bar 6 on the same long side of the base body 61 of the spring bar 6. Furthermore, two spring elements 62 are arranged in the central region of the base body 61 on the opposite longitudinal side of the base body 61 of the spring rod 6.
  • the base body 61 of the spring bar 6 has a polygonal, here cuboid cross-section.
  • Other cross-sectional configurations of the basic body 61 are also conceivable.
  • the reaction forces of the spring elements 62 also act in the vertical direction z, so that the rear side 31a, 31b of the brake pads 3a is caused by the slight rotation of the brake pads 3a, 3b , 3b are also always pressed in the direction of the pressure plate 21 of the pad holder 2.
  • a partial area 35a, 35b adjoining a peripheral edge 33a, 33 of at least one of the brake pads 3a, 3b is an end face at an angle facing the second of the brake pads 3b, 3a a, which is preferably smaller than 2 °, is angled with respect to the remaining end face 34a, 34b of the brake lining 3a, 3b.
  • This angling preferably does not extend over the entire width in the direction y of the brake pads 3a, 3b, but the width of the angled partial area 35a, 35b of the end face of the brake pads 3a, 3b is preferably less than 20% of the total width of the brake pads 3a, 3b.
  • the bend can only be molded on one of the brake pads 3a, 3b. It is also conceivable to provide both brake pads with such a bend in a mirror-image configuration.
  • a tool holder 63 is formed on at least one end of the spring rod 6, at least the rear end in the insertion direction, which is positioned near the locking bolt 25 in the installed state.
  • This tool holder 63 is preferably designed as a bayonet lock recess, so that a correspondingly shaped tool with an angled end can be inserted into the tool holder 63 in a simple manner and the spring rod 6 can thus be pulled out of the receiving channel 5.
  • Such a tool holder is preferably provided at both ends of the base body 61 of the spring bar 6, which enables the spring bar 6 to be installed in the reverse orientation.
  • the angle of rotation of the brake pads 3a, 3b in the inserted state of the spring bar 6 in the receiving channel 5 is preferably about 0.35 °.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Braking Arrangements (AREA)

Abstract

La présente invention concerne un support de garniture de frein pour un frein à disque d'un véhicule ferroviaire comprenant un support de garniture ainsi qu'au moins deux garnitures de frein (3a, 3b) maintenues bloquées sur le support de garniture, ledit support de garniture comportant une plaque d'appui dotée d'un canal de guidage s'étendant dans la direction longitudinale du support de garniture, dans lequel une nervure de guidage (32), disposée côté arrière (31a) des garnitures de frein (3a, 3b) faisant face à la plaque d'appui, est maintenue coulissante, ladite nervure de guidage (32) comportant un canal de réception (5) s'étendant dans une direction de coulissement (x) dans lequel une barre à ressort (6) est reçue, ladite barre à ressort (6) comportant une pluralité d'éléments à ressort (62), qui sont disposés de telle sorte que lorsque la barre à ressort (6) est insérée dans le canal de réception (5), un couple agit sur les garnitures de frein (3a, 3b) perpendiculairement à la direction de coulissement (x) .
EP19795473.8A 2018-11-05 2019-10-17 Support de garniture de frein pour un véhicule ferroviaire Withdrawn EP3877669A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018127475.0A DE102018127475B4 (de) 2018-11-05 2018-11-05 Bremsbelaghalterung für ein Schienenfahrzeug
PCT/EP2019/078290 WO2020094360A1 (fr) 2018-11-05 2019-10-17 Support de garniture de frein pour un véhicule ferroviaire

Publications (1)

Publication Number Publication Date
EP3877669A1 true EP3877669A1 (fr) 2021-09-15

Family

ID=68392946

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19795473.8A Withdrawn EP3877669A1 (fr) 2018-11-05 2019-10-17 Support de garniture de frein pour un véhicule ferroviaire

Country Status (4)

Country Link
EP (1) EP3877669A1 (fr)
CN (1) CN112997020A (fr)
DE (1) DE102018127475B4 (fr)
WO (1) WO2020094360A1 (fr)

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7406362U (de) * 1974-06-06 Knorr Bremse Gmbh Halterung an einem Bremsbelagträger mit einschiebbarem Bremsbelag, insbesondere für Bremsbacken von für Schienenfahrzeuge vorgesehenen Scheibenbremsen
US1493887A (en) * 1923-08-10 1924-05-13 Midura Stanislaw Key for brake shoes and hangers
IT1032231B (it) * 1974-02-23 1979-05-30 Knorr Bremse Gmbh Dispositivo di sopporto per acco gliebo in modo univoco una guar nizione per freni inserible in un sostegno in particolare per cepri di freni a disco per veico li su rotate
DE2547529C2 (de) * 1975-10-23 1982-10-21 Knorr-Bremse GmbH, 8000 München Bremsbacke für Scheibenbremsen
DE2547530A1 (de) * 1975-10-23 1977-04-28 Knorr Bremse Gmbh Bremsbacke fuer scheibenbremsen
DE3417600A1 (de) * 1984-05-11 1985-11-14 Knorr-Bremse GmbH, 8000 München Verschluss zum halten eines in einen bremsbelagtraeger einschiebbaren bremsbelages fuer scheibenbremsen, insbesondere fuer schienenfahrzeuge
FR2611012B1 (fr) * 1987-02-16 1989-05-19 Valeo Garniture de freinage a plots de materiau de friction rapportes
DE19809513C1 (de) * 1998-03-05 1999-11-04 Knorr Bremse Systeme Bremsbelaghalterung für Schienenfahrzeuge
DE102006037802A1 (de) * 2006-08-12 2008-02-14 Bremskerl-Reibbelagwerke Emmerling Gmbh & Co.Kg. Ganzbelagträger für Scheibenbremsbeläge in Schienenfahrzeugen
DE102009006290A1 (de) * 2009-01-27 2010-07-29 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Verbindung eines Bremsbelages mit einem Belaghalter
DE102009060204A1 (de) * 2009-12-23 2011-06-30 Lucas Automotive GmbH, 56070 Scheibenbremse für ein Kraftfahrzeug und Bremsbelaganordnung hierfür
DE102012102584A1 (de) * 2012-03-26 2013-09-26 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Scheibenbremse mit Rückstelleinrichtung und Bremsbelag
DE102013013686A1 (de) * 2013-08-16 2015-02-19 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Belaghaltefeder eines Bremsbelags und Bremsbelaghalterung für eine Scheibenbremse eines Kraftfahrzeugs
US10036437B2 (en) * 2015-11-12 2018-07-31 Bendix Spicer Foundation Brake Llc Disc brake and set of brake pads

Also Published As

Publication number Publication date
DE102018127475A1 (de) 2020-05-07
DE102018127475B4 (de) 2021-05-27
CN112997020A (zh) 2021-06-18
WO2020094360A1 (fr) 2020-05-14

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