EP0941418A1 - Support de frein pour frein a disque a garniture partielle - Google Patents

Support de frein pour frein a disque a garniture partielle

Info

Publication number
EP0941418A1
EP0941418A1 EP97951888A EP97951888A EP0941418A1 EP 0941418 A1 EP0941418 A1 EP 0941418A1 EP 97951888 A EP97951888 A EP 97951888A EP 97951888 A EP97951888 A EP 97951888A EP 0941418 A1 EP0941418 A1 EP 0941418A1
Authority
EP
European Patent Office
Prior art keywords
brake
carrier
support
axially
brake carrier
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Withdrawn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
EP97951888A
Other languages
German (de)
English (en)
Inventor
Peter Schneider
Rolf Weiler
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.)
Continental Teves AG and Co OHG
Original Assignee
Continental Teves AG and Co OHG
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 Continental Teves AG and Co OHG filed Critical Continental Teves AG and Co OHG
Publication of EP0941418A1 publication Critical patent/EP0941418A1/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Withdrawn legal-status Critical Current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
    • 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
    • F16D55/225—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 the braking members being brake pads
    • F16D55/226—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 the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
    • F16D55/2265—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 the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
    • F16D55/227—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 the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing by two or more pins
    • 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
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0008—Brake supports

Definitions

  • the invention relates to a brake carrier for a partial brake disc brake according to the preamble of claim 1.
  • Brake carriers for such partial brake disc brakes are usually either integrated into the steering knuckle of a motor vehicle or fastened to it.
  • a brake housing, which surrounds the edge of the brake disk and on both sides of the brake disk, is axially displaceably mounted on the brake carrier.
  • Generic brake carriers are known in a variety of embodiments.
  • DE 44 31 724 AI discloses a disc brake which has a brake carrier which has axially protruding brake support arms.
  • guide sections are provided on the brake support arms, on which the two brake pads are supported and guided in an axially displaceable manner.
  • the brake pads with lateral support parts in the circumferential direction engage in a form-fitting manner in the guide sections of the brake support arms in such a way that the friction forces absorbed by the brake pads are transmitted to both brake support arms at least with higher brake system forces.
  • there is a not inconsiderable elastic deformation of the brake support arms in the circumferential direction which has a particularly strong effect due to the lever arms at the axially outer end of the brake support arms.
  • the resulting misalignment of the brake arms in the circumferential direction also affects the housing via the brake pads and thus leads to an undesired misalignment of the brake housing and the two brake pads.
  • the invention has therefore set itself the task of preventing or reducing the misalignment of the brake housing, in particular of the brake support arms, by measures on the brake carrier.
  • the solution to the object is achieved by the combination of features of claim 1.
  • the elasticity of the brake support-side lining support of the inner brake lining is increased by the material rigidity of the brake support arm in the U direction of the axially inner lining support is specifically reduced.
  • the housing misalignment has been reduced considerably.
  • the brake linings are supported in a form-fitting manner on the brake support arms in the circumferential direction in such a way that the frictional force occurring in the circumferential direction on the brake linings is transmitted to both brake support arms at least with higher brake application forces.
  • a brake carrier with pull-push support of the brake pads can be specifically designed with a suitable choice of the tolerance field for brake pads and pad supports such that a noise-resistant pull design of the brake pads is selected for small brake application forces, while with high braking forces due to the elasticity the pad supports a push-pull support for both brake pads can be guaranteed.
  • the axially inner lining support is formed on an essentially axially extending web which is connected in one piece to the brake carrier arm.
  • An essentially axially extending recess remains between this web and the brake carrier arm, as a result of which the web with lining support is elastically flexible in the circumferential direction.
  • the same flexibility in the circumferential direction under load can be set for the inner as for the outer lining support.
  • Such measures on brake carriers can extend both to a single brake carrier arm (push or pull support) and to both brake carrier arms (push-pull support).
  • the measures on the brake carrier are carried out directly when the brake carrier blank is cast, the essential dimensions of the brake carrier being able to be retained in comparison with known designs.
  • At least one guide pin for axially displaceable mounting of the brake housing is attached directly to the inner lining support, which is elastically flexible in the circumferential direction.
  • the guide pins follow the deformation of the brake support arms or, in particular, the deformation in the region of the axially inner lining support, by parallel displacement in the circumferential direction, and thus prevent the brake housing from being skewed.
  • 1 is a three-dimensional rear view of a brake carrier with circumferentially elastic pad support of the inner brake pad
  • FIG. 2 shows a three-dimensional top view of the brake carrier from FIG. 1.
  • a brake pad brake consists essentially of a base section 2 which extends in a secant direction of the brake disk (not shown) and two brake support arms 3 which adjoin the lateral ends of the base section 2 and which in the axial direction have the outer edge protrude from a brake disc, not shown.
  • the base section 2 can be screwed through two through holes 4, in particular on the steering knuckle of a motor vehicle.
  • the spaced-apart parallel brake support arms 3 are integrally connected to the base section 2 and are used for axially displaceable guidance and support of brake pads, not shown.
  • axial guide grooves 5 are formed in the brake support arms 3, which are open to the outside in the radial direction.
  • the brake pads engage with hook-shaped, lateral support parts in the guide grooves 5 and thus allow the frictional force occurring on the brake pads in the circumferential direction to be transmitted to both brake support arms 3.
  • this is realized by means of support surfaces 6 oriented perpendicular to the circumferential direction within the guide grooves 5.
  • the support surfaces 6 facing or facing away from the brake center, together with correspondingly oriented contact surfaces on the non- brake pads showed a pulling (Pull) and / or pushing (Push) support of the two brake pads.
  • the pad support 7 for the axially outer brake pad is subject to a certain elasticity anyway due to the lever arms of the brake carrier arm 3.
  • the axially inner pad support 8 is formed on a substantially axially extending web 9.
  • the web 9 is connected in one piece to the brake carrier arm 3 and has an elastic flexibility in the radial as well as in the tangential direction when loaded. In the circumferential direction, an axially extending recess 10 remains between the web 9 and the brake carrier arm 3.
  • the inner lining support 8 in the brake carrier 1 from FIG. 1 can be deformed elastically in the circumferential direction considerably more easily.
  • the inevitable deformation, in particular of the brake support arms 3 in known brake support designs, was manifested in particular in an inclined position of the brake support arms 3 in Direction of rotation of the brake disc.
  • Such an inclination has a very strong effect on the axially outer lining supports 7 in the form of a tangential displacement.
  • the elastic resilience in the circumferential direction of the inner lining support 8 can be adapted to that of the outer lining support 7 by targeted constructive design of the web 9 and the recess 10.
  • undesired oblique wear on the brake linings and a resulting stronger tendency to brake noises for a wide variety of brake types with generic brake carriers can be avoided.
  • the deliberate push-pull design of both brake linings can be facilitated in the case of partial brake pads of this type of brake.
  • Another advantage results from arranging the guide bolts (not shown) attached to the brake carrier 1 in the immediate vicinity of the inner lining support 8, which is elastic in the circumferential direction, on the brake carrier 1.
  • two guide bolts are screwed into threaded bores 11 of fastening eyes 12 on the base section 2.
  • the spaced axially oriented guide pins are axially displaceable within bores of the brake housing, not shown.
  • the arrangement of the fastening eyes 12 for the guide bolts directly on the inner lining support 8 results in a considerable reduction in the misalignment of the brake housing when high braking peripheral forces are absorbed by the brake carrier 1.
  • the design of the web 9 or the recess 10 is formed directly in the configuration of the brake carrier blank 1 produced by casting. This avoids additional machining operations. At first, nothing is changed in the basic dimensions of the brake carrier 1 by the design measures according to the invention. The existing processing steps on the cast blank can be maintained using existing tools or machines.
  • the configuration of the elastic support which is the same in the circumferential direction, for the inner as well as the outer brake lining is of course not limited to the exemplary embodiment shown in the figures.
  • the reduction in the material stiffness of the inner lining support 8 can, depending on the type of lining support selected, also be achieved exclusively on the inlet and outlet side brake support arm 3. This means that the principle can be implemented for any type of base support.

Landscapes

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

Abstract

L'invention concerne un frein à disque à garniture partielle, comportant un support de frein (1), qui est de préférence vissé sur la fusée d'essieu, et un carter de frein qui est monté de façon à pouvoir se déplacer axialement par rapport au support de frein et entoure un disque de frein et les plaquettes de frein placées de chaque côté de ce dernier, plaquettes qui sont guidées de façon à pouvoir se déplacer axialement et qui reposent dans des sections de guidage formées spécialement, sur les branches de support de frein (3) qui font saillie axialement sur le disque de frein. Selon l'invention, afin d'empêcher une inclinaison non désirée des branches de support de frein (3) due à des forces de freinage périphériques importantes, ou bien pour empêcher l'inclinaison du carter de frein complet qui pourrait en résulter, les supports de plaquette intérieur et extérieur (7, 8) sont formés de façon à présenter la même élasticité dans le sens périphérique. Ainsi, lorsque les plaquettes de frein subissent des forces de freinage périphériques, les supports de plaquettes (7, 8) sont déplacés sensiblement dans le même sens et parallèlement, de façon élastique, dans le sens de rotation du disque de frein. Une usure oblique non désirée des plaquettes ou une inclinaison du carter de frein peuvent, grâce à cet agencement, être empêchées ou réduites avec succès.
EP97951888A 1996-12-05 1997-11-12 Support de frein pour frein a disque a garniture partielle Withdrawn EP0941418A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE1996150425 DE19650425B4 (de) 1996-12-05 1996-12-05 Bremsträger für eine Teilbelagscheibenbremse
DE19650425 1996-12-05
PCT/EP1997/006303 WO1998025044A1 (fr) 1996-12-05 1997-11-12 Support de frein pour frein a disque a garniture partielle

Publications (1)

Publication Number Publication Date
EP0941418A1 true EP0941418A1 (fr) 1999-09-15

Family

ID=7813704

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97951888A Withdrawn EP0941418A1 (fr) 1996-12-05 1997-11-12 Support de frein pour frein a disque a garniture partielle

Country Status (4)

Country Link
EP (1) EP0941418A1 (fr)
JP (1) JP2001509233A (fr)
DE (1) DE19650425B4 (fr)
WO (1) WO1998025044A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10004182A1 (de) * 2000-02-01 2001-08-02 Continental Teves Ag & Co Ohg Scheibenbremseinheit, insbesondere Teilbelag-Scheibenbremse für Kraftfahrzeuge
DE10314437A1 (de) * 2003-03-31 2004-10-14 Continental Teves Ag & Co. Ohg Bremsträger für eine Teilbelagscheibenbremse
DE10358086A1 (de) * 2003-12-10 2005-07-14 Continental Teves Ag & Co. Ohg Teilbelagscheibenbremse mit zusätzlicher Versteifung der äußeren Belagabstützung
CN101947592B (zh) * 2010-08-24 2012-10-24 包头北方创业股份有限公司 制动梁拉伸防裂装置
DE102016104967A1 (de) 2015-10-09 2017-04-13 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Bremsträger

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2804808B2 (de) * 1978-02-04 1981-04-16 Alfred Teves Gmbh, 6000 Frankfurt Bremsbackenhalterung für eine Teilbelagscheibenbremse, insbesondere für Kraftfahrzeuge
JPS54109575A (en) * 1978-02-16 1979-08-28 Nissan Motor Co Ltd Disc brake
DE8809123U1 (fr) * 1988-07-15 1989-11-16 Lucas Industries P.L.C., Birmingham, West Midlands, Gb
US5022500A (en) * 1988-09-14 1991-06-11 Brake And Clutch Industries Australia Pty. Ltd. Disc brake caliper
DE3913904A1 (de) * 1989-04-27 1990-10-31 Teves Gmbh Alfred Schwimmsattel-scheibenbremse, insbesondere fuer kraftfahrzeuge
DE4431724B4 (de) * 1994-09-06 2004-07-29 Continental Teves Ag & Co. Ohg Schwimmsattel für Scheibenbremse

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9825044A1 *

Also Published As

Publication number Publication date
JP2001509233A (ja) 2001-07-10
DE19650425B4 (de) 2007-04-05
DE19650425A1 (de) 1998-06-10
WO1998025044A1 (fr) 1998-06-11

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