WO2016046065A1 - Fixation de garniture de frein d'un frein à disque, frein à disque et garniture de frein - Google Patents

Fixation de garniture de frein d'un frein à disque, frein à disque et garniture de frein Download PDF

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Publication number
WO2016046065A1
WO2016046065A1 PCT/EP2015/071388 EP2015071388W WO2016046065A1 WO 2016046065 A1 WO2016046065 A1 WO 2016046065A1 EP 2015071388 W EP2015071388 W EP 2015071388W WO 2016046065 A1 WO2016046065 A1 WO 2016046065A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
lining
spring element
brake pad
carrier
Prior art date
Application number
PCT/EP2015/071388
Other languages
German (de)
English (en)
Inventor
Schönauer SCHÖNAUER
Josef Schropp
Original Assignee
Knorr-Bremse Systeme für Nutzfahrzeuge 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 für Nutzfahrzeuge GmbH filed Critical Knorr-Bremse Systeme für Nutzfahrzeuge GmbH
Priority to EP15763932.9A priority Critical patent/EP3198165A1/fr
Publication of WO2016046065A1 publication Critical patent/WO2016046065A1/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
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • F16D65/0972—Resilient means interposed between pads and supporting members or other brake parts transmitting brake reaction force, e.g. elements interposed between torque support plate and pad
    • 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
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • F16D65/0973—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces
    • F16D65/0974—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces acting on or in the vicinity of the pad rim in a direction substantially transverse to the brake disc axis
    • F16D65/0977—Springs made from sheet metal
    • F16D65/0978—Springs made from sheet metal acting on one pad only
    • 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
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/54—Slack adjusters mechanical self-acting in one direction for adjusting excessive play by means of direct linear adjustment
    • 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
    • F16D2065/13—Parts or details of discs or drums
    • F16D2065/134—Connection
    • F16D2065/1392—Connection elements
    • F16D2065/1396—Ancillary resilient elements, e.g. anti-rattle or retraction springs

Definitions

  • the present invention relates to a brake pad holder of a disc brake of a motor vehicle, in particular a commercial vehicle, according to the preamble of claim 1 and a disc brake and a brake pad.
  • the brake linings are based on these brake carrier horns, depending on the direction of rotation of the brake disc.
  • the inlet-side carrier horn while the rear carrier horn is called in a main direction of rotation of the brake disc, so the direction of rotation of the brake disc during a forward drive of the motor vehicle.
  • the front carrier horn is referred to as the outlet side carrier horn in a main direction of rotation of the brake disc, so the direction of rotation of the brake disc during a forward drive of the motor vehicle.
  • the known from the prior art brake pads usually have on their side facing away from the axis of rotation of the brake disc upper edge of a pad retaining spring, which is supported via a lining shaft opening of the brake caliper spanning pad holder radially outward.
  • This pad retaining spring serves on the one hand to compensate for tolerances occurring and for damping the brake pads to protect against jerky load that can damage the connection of the friction mass to the lining carrier plate.
  • the pad retaining springs also serve to reduce rattling noise of the brake pads during driving. In the absence of the movable bearing between the caliper and the brake carrier and the simultaneous connection of the brake caliper with the brake pads or the brake pads would also contribute to the above-mentioned forces acting on the respective support surfaces between the brake pad and brake carrier, in particular as reaction force in Rüttelbelas- lines.
  • the brake carrier In order to prevent such an oblique wear, the brake carrier would have to be replaced, which would be associated with high material and processing costs. In order to prevent digging of the brake pads in the contact surfaces of the brake carrier, it is known to harden the brake carrier horns. However, this measure is associated with a high production and cost. In addition, this method can lead to a distortion of the brake carrier, which would jeopardize the maintenance of function-relevant tolerances and, where possible, would result in a more difficult mounting of the brake.
  • a disc brake is known in which by a special shape of the brake pads and the wearer carrier of the brake carrier and the kinematic design and the ratios of the attacking force components, these disc brakes are able to brakes in both the brakes discontinuously positioned brake carrier horns as well as via a positive connection directly into the einlaufsei- positioned brake carrier horns or detours via friction and higher reaction forces in the brake or the brake carrier to initiate.
  • This positive connection between the brake pad and the brake carrier on the inlet side carrier horn can be prevented at a forward braking decelerating braking operation with simultaneous positive connection of the caliper with at least one of the brake pads.
  • Object of the present invention is to develop a generic brake pad holder such that with an acceptable bias of the brake pads both a slight displaceability of the caliper is guaranteed as well as an acceptable damping of the caliper and a To ensure protection of the heavily loaded support surfaces between the brake pads and the brake carrier horns.
  • a brake pad is spring-loaded on at least one side of a brake disc, a brake pad in a lining shaft of a stationary brake carrier with the brake lining laterally enclosing brake carrier horns.
  • the brake pad has at least one friction lining and a lining carrier plate carrying the friction lining. From an inlet-side edge of the lining carrier plate, a projection which projects in the assembled state of the brake lining in a lateral recess of an inlet-side carrier horn of the brake carrier extends.
  • a spring element is arranged with two elastic ends.
  • a first end of the spring element is designed so as to support the brake pad radially relative to an axis of rotation of the brake disc close foot region of the inlet side carrier horn to the axis of rotation of the brake disc.
  • a second end of the spring element is designed to support the brake pad with respect to a rotational axis of the brake disc remote support the head portion of the inlet side carrier horn radially to the axis of rotation of the brake disc.
  • the spring element is positively or non-positively fixed to the inlet side carrier horn.
  • two of the inlet side carrier horn encompassing first tabs are particularly preferably formed. Such tabs can be formed on the spring element in a simple manner.
  • as a simple assembly and management of the spring element on the inlet side carrier horn allows.
  • the first end of the spring element is preferably supported in the mounted state on one of the axis of rotation of the brake disc facing functional surface of the lining carrier plate as functional surfaces serve preferably the axis of rotation of the brake disc facing bottom of the projection and / or a region of the lining carrier plate, which extends below the projection for the axis of rotation of the brake disc facing the lower edge of the lining carrier plate extending toward.
  • the second end of the spring element is preferably formed bent in the head region of the inlet side carrier horn.
  • the unloaded state is the second end of the spring element on the head portion of the inlet side carrier horn while it just bent in the loaded state against the spring force of the second end between the head portion of the inlet side carrier horn and the edge of the brake pad 2 rests and so not alone from the first end of the spring element Catchable vibrations dampened.
  • the spring element is formed according to a further preferred embodiment as a leaf spring or wire spring and thus easy and inexpensive to produce and particularly suitable for installation in a narrow gap between the inlet side carrier horn and the inlet side horn facing side horn of the brake pad.
  • the first end of the spring element is preferably arc-shaped, in particular s-shaped.
  • a head region of the intake side Bremschihorns near edge of the lining carrier plate is formed with a radially from the brake carrier horn radially from the axis of rotation of the brake disc increasingly removing contour.
  • the spring element in the application direction of the brake pad is slidably fixed to the lining carrier plate. This has the advantage that with each brake pad change a new spring element must be mounted necessarily, and thus optimal function of the caliper guide over the life of the brake is guaranteed.
  • two second lugs embracing the lining carrier plate are preferably formed on the spring element. These tabs preferably have holes for receiving a fixed to the lining carrier plate connecting element.
  • the spring element has a slot-shaped recess in the application direction of the brake lining for receiving a connecting element fixed to the lining carrier plate.
  • the surface of the spring element is hardened according to a further advantageous embodiment variant. This results in the area of the brake carrier horns, which are preferably made of cast material, a further improved protection against burial.
  • the disc brake according to the invention of a motor vehicle, in particular of a commercial vehicle, is distinguished by the brake pad holder having the abovementioned features.
  • the brake pad according to the invention of a disc brake of a motor vehicle, in particular a commercial vehicle, which has a friction lining and a lining carrier plate carrying the friction lining and in which a projection extends from an inlet side edge of the lining carrier plate, which in the assembled state of the brake lining in a lateral recess of a einlaufseiti - Gen Marshhorns a brake carrier of the disc brake projects, is characterized in that on the inlet side edge of the lining carrier plate, a spring element is arranged with two elastic ends.
  • a first end of the spring element is designed such that it supports the brake lining with respect to a rotational axis of a brake disc near foot region of the inlet side carrier horn radially to the axis of rotation of the brake disc.
  • the second end of the spring element is designed in such a way, the brake pad relative to a head portion remote from an axis of rotation of the brake disc support the inlet side carrier horn radially to the axis of rotation of the brake disc.
  • FIG. 1 shows a side view of a detail of a disk brake with a brake carrier and a brake pad mounted between carrier horns of the brake carrier,
  • FIG. 2 is a perspective view of that shown in FIG.
  • FIG. 3 in a state mounted on respective brake carrier horns, a perspective view of a brake lining with an alternative embodiment variant of a spring element arranged thereon, a perspective view of the spring element shown in FIG.
  • Figure 7 is a perspective view of a brake pad with assumed spring element.
  • the reference numeral 1 designates a brake carrier of a disc brake of a motor vehicle, in particular of a commercial vehicle, the brake carrier 1 essentially comprises a base body 11 and carrier horns 12, 13 arranged on the outlet side and outlet side, between which Brake pad 2 is held.
  • the brake pad 2 has at least one friction lining 22 and a lining carrier plate carrying the friction lining 22, as shown by way of example in FIG.
  • a (not shown) disc brake disc facing away from the edge 28 of the lining carrier plate 21 is a lining holder spring 4 is verliergesichtert and held radially deflectable.
  • This pad retaining spring 4 is here, contrary to the usual positioning centered on the edge 28 of the pad carrier plate 21 here in the region of the outlet side carrier horn 13 facing half of the edge 28 of the pad carrier plate 21 positioned.
  • This pad retaining spring 4 is supported radially upwards on a pad retainer (also not shown) spanning the pad shaft of a caliper, not shown, which is detachably fixed to a brake caliper, not shown, of the disc brake, for example.
  • the brake carrier 1 itself is fixedly mounted on the vehicle housing or a component of the vehicle axle.
  • the brake disk (not shown) rotates together with a wheel axle of the motor vehicle during a forward movement of the motor vehicle in a main direction of rotation D.
  • a spring element is disposed between the inlet side edge of the lining carrier plate 21 and the inlet side brake horn 12 3 arranged.
  • This spring element 3 has two elastic ends 31, 31, which are connected to each other by one of the contour of the inlet-side edge of the lining carrier plate 21 following Mitteilteil.
  • the spring element 3 is designed as a leaf spring in the embodiment variant shown here. Also conceivable is the design of the spring element 3 as a wire spring.
  • a projection 23 which, in the assembled state of the brake lining 2, protrudes into a lateral recess 14 of the inlet-side carrier horn 12 of the brake carrier 1, so that the brake lining 2 is moved by a pivoting movement into the running side carrier horn 12 and the outlet side carrier horn 13 in the circumferential direction of the brake disc limited lining shaft of the brake carrier is used.
  • the first end 1 of the spring element is designed to support the brake pad 2 with respect to an axis of rotation of the brake disc near foot region 15 of the inlet side carrier horn 12 radially to the axis of rotation of the brake disc.
  • this first end 31 of the spring element 3 is preferably arcuate, in particular S-shaped.
  • an end piece of the first end 31 is supported on a functional surface 27 of the carrier plate 21.
  • this functional surface 27 is formed as a slightly beveled region extending towards the inlet-side edge of the lining carrier plate 21, in relation to the circumference of the brake disk extending towards the rotational axis of the brake disk.
  • Another functional surface 26 of the carrier plate is formed by the underside of the projection 23 facing the axis of rotation of the brake disk, against which a supporting surface 36 of the spring element 3 abuts.
  • the spring element is bent here s-shaped, the lower arc rests on the foot portion 15 of the inlet side carrier horn 12 and thereby the brake pad 2 on the inlet side Bremsharihorn 12 resiliently supported.
  • a second end 31 of the spring element 3 is designed to radially displace the brake pad 2 against a head region 16 of the inlet side carrier horn 12, which is remote from an axis of rotation of the brake disc Support the axis of rotation of the brake disc.
  • the second end 32 of the spring element 3 is, as can be clearly seen in FIGS. 1 and 2, formed bent toward the head region 16 of the inlet-side carrier horn 12.
  • the second end 32 is in the unloaded state at the head portion 16 of the inlet side carrier horn. In the loaded state, the second end 32 is pressed against the spring force of the second end 32 just bent between the head portion 16 of the inlet-side carrier horn 12 and the edge of the brake pad 2. Since the second end 32 of the spring element 3 is particularly preferably designed to be relatively short, a significantly higher force is required for straight bending of this bent second end 32 than for deformation of the first end 31 of the spring element 3. Thus, a total of two-step cushioning of the brake pad 2 by the Spring element 3 allows.
  • the spring element 3 is positively or non-positively fixed to the inlet side carrier horn 12.
  • the spring element 3 two the inlet side carrier horn 12 embracing first tabs 35 are integrally formed.
  • the spring element 3 in the application direction Z of the brake pad 2 slidably on the lining carrier plate 21 can be fixed.
  • a slot-shaped recess 39 extending in the application direction Z of the brake pad 2, in particular in the form of an elongated hole, is provided on a surface piece 34 of the spring element 3 resting on the inlet side edge of the lining carrier plate 21.
  • this slot-shaped recess 39 is fixed to the lining carrier plate 21 connecting element 5 with a head piece whose diameter is greater than the slot width of the slot 39, is added.
  • a displacement of the lining carrier plate 21 relative to the spring element 3 held stationary in the application direction Z is made possible.
  • a second tab 37 is formed on the Abstütz- surface 34 of the spring element 3, which surrounds the lining carrier plate 21 of at least one side.
  • a connecting element 5 is fixed in the lining carrier plate 21, in this case on a side parallel to the friction surface of the brake disc back of the lining carrier plate, which is received in a bore 38 of the second tab 37.
  • the second tab 37 with increasing wear of the friction lining 22 from the friction lining 22 facing away from the rear side of the support plate 21 continue to remove.

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

Abstract

L'invention concerne une fixation de garniture de frein d'un frein à disque de véhicule à moteur, en particulier d'un véhicule utilitaire, sur au moins une face d'un frein à disque de frein, une garniture de frein (2) étant logée sollicitée par ressort dans un logement de garniture d'un support de frein (1) doté de cornes de support de frein (12, 13) enserrant la garniture de frein (2) latéralement, ladite garniture de frein (2) présentant au moins une garniture de friction (22) et une plaque de support de garniture (21) portant ladite garniture de friction (22), A l'état monté de la garniture de frein (2), une partie saillante (23) qui part du bord de la plaque de support de garniture (21), situé côté entrée, fait saillie dans une cavité latérale (14) d'une corne de support (12) du support de frein (1), située côté entrée. Un élément ressort (3) comportant deux extrémités élastiques (31, 32) est disposé entre ledit au moins un bord de la plaque support de garniture (21), situé côté entrée, et la corne de support de frein (12), située côté entrée. Une première extrémité (31) de l'élément ressort (3) est conçue de manière à soutenir, radialement par rapport à l'axe de rotation du disque de frein, la garniture de frein (2) vis-à-vis d'une zone de base de la corne de support (12), située côté entrée, ladite zone de base se trouvant à proximité d'un axe de rotation du disque de frein, et une seconde extrémité (31) de l'élément ressort (3) est conçue de manière à soutenir la garniture de frein (2), radialement par rapport à l'axe de rotation du disque de frein, vis-à-vis d'une zone de tête (16) de la corne de support (12), côté entrée, ladite zone de tête étant éloignée de l'axe de rotation du disque de frein. L'invention concerne en outre un frein à disque et une garniture de frein d'un frein à disque de véhicule à moteur.
PCT/EP2015/071388 2014-09-22 2015-09-18 Fixation de garniture de frein d'un frein à disque, frein à disque et garniture de frein WO2016046065A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP15763932.9A EP3198165A1 (fr) 2014-09-22 2015-09-18 Fixation de garniture de frein d'un frein à disque, frein à disque et garniture de frein

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014113617.9A DE102014113617A1 (de) 2014-09-22 2014-09-22 Bremsbelaghalterung einer Scheibenbremse, Scheibenbremse und Bremsbelag
DE102014113617.9 2014-09-22

Publications (1)

Publication Number Publication Date
WO2016046065A1 true WO2016046065A1 (fr) 2016-03-31

Family

ID=54145782

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2015/071388 WO2016046065A1 (fr) 2014-09-22 2015-09-18 Fixation de garniture de frein d'un frein à disque, frein à disque et garniture de frein

Country Status (3)

Country Link
EP (1) EP3198165A1 (fr)
DE (1) DE102014113617A1 (fr)
WO (1) WO2016046065A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017129672A1 (de) * 2017-12-12 2019-06-13 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Scheibenbremse für ein Nutzfahrzeug und Bremsbelagsatz
DE102022200654A1 (de) 2022-01-20 2023-07-20 Hl Mando Corporation Bremsbelaganordnung mit einer Belagfeder für ein Scheibenbremssystem und Scheibenbremssystem
DE102022101381A1 (de) 2022-01-21 2023-07-27 Bpw Bergische Achsen Kommanditgesellschaft Scheibenbremse

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2017236A (en) * 1978-03-23 1979-10-03 Volkswagenwerk Ag Disc Brake of the Floating Calliper Type
FR2800140A1 (fr) * 1999-10-26 2001-04-27 Bosch Gmbh Robert Ressort de guidage d'elements de friction et frein a disque comportant au moins un tel ressort
US20050241897A1 (en) * 2004-04-29 2005-11-03 Robert Bosch Gmbh System for fitting disk brake pads and disk brake comprising such a system
US20050274579A1 (en) * 2004-06-14 2005-12-15 Akebono Brake Industry Co., Ltd. Pad clip of disc brake apparatus

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH1182570A (ja) * 1997-09-16 1999-03-26 Tokico Ltd ディスクブレーキ
JP3303780B2 (ja) * 1998-07-08 2002-07-22 住友電気工業株式会社 ディスクブレーキ
JP2001193769A (ja) * 1999-12-14 2001-07-17 Continental Teves Ag & Co Ohg 自動車用部分パッド型ディスクブレーキ
FR2851310B1 (fr) * 2003-02-17 2006-04-28 Bosch Gmbh Robert Organe de friction et frein a disque pour vehicule automobile muni de cet organe de friction
JP2006097739A (ja) * 2004-09-28 2006-04-13 Taga Seisakusho:Kk ばね板の撓み量計算方法
JP4589190B2 (ja) * 2005-07-28 2010-12-01 日立オートモティブシステムズ株式会社 ディスクブレーキ
JP4650400B2 (ja) * 2006-11-20 2011-03-16 トヨタ自動車株式会社 ディスクブレーキ装置
EP2570689B2 (fr) 2011-09-14 2021-09-22 KNORR-BREMSE Systeme für Nutzfahrzeuge GmbH Frein à disque d'un véhicule automobile et garniture de frein

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2017236A (en) * 1978-03-23 1979-10-03 Volkswagenwerk Ag Disc Brake of the Floating Calliper Type
FR2800140A1 (fr) * 1999-10-26 2001-04-27 Bosch Gmbh Robert Ressort de guidage d'elements de friction et frein a disque comportant au moins un tel ressort
US20050241897A1 (en) * 2004-04-29 2005-11-03 Robert Bosch Gmbh System for fitting disk brake pads and disk brake comprising such a system
US20050274579A1 (en) * 2004-06-14 2005-12-15 Akebono Brake Industry Co., Ltd. Pad clip of disc brake apparatus

Also Published As

Publication number Publication date
DE102014113617A1 (de) 2016-03-24
EP3198165A1 (fr) 2017-08-02

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