WO1998025044A1 - Brake carrier for a partially lined disc brake - Google Patents

Brake carrier for a partially lined disc brake Download PDF

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Publication number
WO1998025044A1
WO1998025044A1 PCT/EP1997/006303 EP9706303W WO9825044A1 WO 1998025044 A1 WO1998025044 A1 WO 1998025044A1 EP 9706303 W EP9706303 W EP 9706303W WO 9825044 A1 WO9825044 A1 WO 9825044A1
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WO
WIPO (PCT)
Prior art keywords
brake
carrier
support
axially
brake carrier
Prior art date
Application number
PCT/EP1997/006303
Other languages
German (de)
French (fr)
Inventor
Peter Schneider
Rolf Weiler
Original Assignee
Continental Teves Ag & 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 & Co. Ohg filed Critical Continental Teves Ag & Co. Ohg
Priority to JP52511398A priority Critical patent/JP2001509233A/en
Priority to EP97951888A priority patent/EP0941418A1/en
Publication of WO1998025044A1 publication Critical patent/WO1998025044A1/en

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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.

Abstract

The invention concerns a partially lined disc brake with a brake carrier (1), which is preferably screwed on the stub axle, and with a brake housing which is mounted so as to be axially displaceable relative to the brake carrier and surrounds a brake disc and brake pads disposed on either side of the latter, the brake pads being guided in an axially displaceable manner and supported in specially designed guide sections on the brake carrier arms (3) which project axially over the brake disc. According to the invention, in order to prevent the undesired inclination of the brake carrier arms (3) as a result of intensive peripheral braking forces or the resultant inclination of the entire brake housing, the inner and outer pad supports (7, 8) are formed so as to be resiliently flexible to an equal extent in the peripheral direction. As a result, when the brake pads are stressed by peripheral braking forces, the pad supports (7, 8) are displaced substantially in the same direction in a resilient and parallel manner in the sense of rotation of the brake disc. Undesired sloping wear on the pads or an inclination of the brake housing can be successfully prevented or reduced owing to this measure.

Description

Bremsträger für eine TeilbelagscheibenbremseBrake carrier for a partial brake disc brake
Die Erfindung betrifft einen Bremsträger für eine Teilbelagscheibenbremse gemäß dem Oberbegriff des Patentanspruchs 1. Bremsträger für derartige Teilbelagscheibenbremsen sind üblicherweise entweder in den Achsschenkel eines Kraftfahrzeuges integriert oder aber an diesem befestigt. Am Bremsträger ist ein den Rand der Bremsscheibe und beiderseits der Bremsscheibe angeordnete Bremsbeläge umgreifendes Bremsgehäuse axial verschiebbar gelagert. Gattungsgemäße Bremsträger sind in einer Vielzahl von Ausführungsformen bekannt.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.
So offenbart die DE 44 31 724 AI eine Scheibenbremse, die einen Bremsträger aufweist, der die Bremsscheibe axial überragende Bremstragerarme besitzt. Dabei sind an den Bremstragerarmen Führungsabschnitte vorgesehen, an denen die beiden Bremsbeläge axial verschiebbar abgestützt und geführt werden. Im einzelnen greifen die Bremsbeläge mit in Umfangsrichtung seitlichen Tragteilen derart formschlüssig in die Führungsabschnitte der Bremstragerarme ein, daß zumindest bei höheren Bremsanlagekräften die von den Bremsbelägen aufgenommenen Reibkräfte auf beide Bremstragerarme übertragen werden. Insbesondere bei hohen Bremsanlegekräften kommt es dabei zu einer nicht unerheblichen elastischen Verformung der Bremstragerarme in Umfangsrichtung, die sich aufgrund der Hebelarme am axial äußeren Ende der Bremstragerarme besonders stark auswirkt. Die sich daraus ergebende Schiefstellung der Bremstr gerarme in Umfangsrichtung wirkt sich über die Bremsbeläge auch auf das Gehäuse aus und führt damit zu einer unerwünschten Schiefstellung des Bremsgehäuses sowie der beiden Bremsbeläge. Der daraus resultierende Schrägverschleiß an den Bremsbelägen bewirkt neben einer Verschlechterung der Funktion auch eine Verschlechterung des Komfortverhaltens der Bremse. Insbesondere ist die Scheibenbremse bei Schrägverschleiß empfindlicher für die Entstehung von Bremsgeräuschen.For example, DE 44 31 724 AI discloses a disc brake which has a brake carrier which has axially protruding brake support arms. In this case, guide sections are provided on the brake support arms, on which the two brake pads are supported and guided in an axially displaceable manner. In particular, 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. Particularly with high brake application 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 resulting oblique wear on the In addition to a deterioration in function, brake pads also deteriorate the comfort behavior of the brake. In particular, the disc brake is more sensitive to the occurrence of braking noises in the case of inclined wear.
Die Erfindung hat sich daher die Aufgabe gesetzt, durch Maßnahmen am Bremsträger die Schiefstellung des Bremsgehäuses insbesondere der Bremstragerarme zu verhindern bzw. zu reduzieren.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.
Erzielt wird die Lösung der Aufgabe durch die Merkmalskombination des Patentanspruchs 1. Dazu wird die Elastizität der bremsträgerseitigen Belagabstützung des inneren Bremsbelages gesteigert, indem die Materialsteifigkeit des Bremsträgerarmes in U fangsrichtung an der axial inneren Belagabstützung gezielt herabgesetzt wird. Daraus ergibt sich für den inneren wie für den äußeren Bremsbelag eine in Umfangsrichtung annähernd gleiche elastische Abstützung am Bremsträgerarm und daher eine fast gleiche elastische Verformung der Bremstragerarme bei Bremseneingriff. Als Ergebnis dieser Maßnahme ist eine ganz erhebliche Reduzierung der Gehäuseschiefstellung zu verzeichnen.The solution to the object is achieved by the combination of features of claim 1. For this purpose, 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. This results in an approximately identical elastic support on the brake support arm in the circumferential direction for the inner and for the outer brake lining and therefore an almost identical elastic deformation of the brake support arms when the brake engages. As a result of this measure, the housing misalignment has been reduced considerably.
In einer bevorzugten Ausführungsform der Erfindung sind die Bremsbeläge in Umfangsrichtung derart formschlüssig an den Bremstragerarmen abgestützt, daß zumindest bei höheren Bremsanlegekräften die an den Bremsbelägen in Umfangsrichtung auftretende Reibungskraft auf beide Bremstragerarme übertragen wird. Ein derartiger Bremsträger mit Pull-Push-Abstützung der Bremsbeläge kann bei geeigneter Wahl der Toleranzfeider für Bremsbeläge und Belagabstützungen gezielt derart ausgelegt werden, daß bei kleinen Bremsanlegekräften eine geräuschunempfindliche Pull-Auslegung der Bremsbeläge gewählt wird, während bei hohen Bremskräften durch die Elastizität der Belagabstützungen eine Push-Pull-Abstützung für beide Bremsbeläge garantiert werden kann.In a preferred embodiment of the invention, 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. Such 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.
In einer vorteilhaften Ausführung des Bremsträgers ist die axial innere Belagabstützung an einem im wesentlichen axial verlaufenden, einstückig mit dem Bremsträgerarm verbundenen Steg ausgebildet. Zwischen diesem Steg und dem Bremsträgerarm verbleibt dabei eine im wesentlichen axial sich erstreckende Ausnehmung, wodurch der Steg mit Belagabstützung in Umfangsrichtung elastisch nachgiebig ist. Durch gezielte Auslegung der Elastizität des Steges mit innerer Belagabstützung kann für die innere wie für die äußere Belagabstützung die gleiche Nachgiebigkeit in Umfangsrichtung bei Belastung eingestellt werden. Dabei können sich derartige Maßnahmen an Bremsträgern sowohl auf einen einzigen Bremsträgerarm (Push- oder Pull- Abstützung) als auch auf beide Bremstragerarme (Push-Pull- Abstützung) erstrecken. Im einzelnen werden die Maßnahmen am Bremsträger unmittelbar beim Gießen des Bremsträgerrohlings vorgenommen, wobei die wesentlichen Abmessungen des Bremsträgers im Vergleich zu bekannten Ausführungen beibehalten werden können .In an advantageous embodiment of the brake carrier, 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. By specifically designing the elasticity of the web with inner lining support, 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). In particular, 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.
In einer Weiterentwicklung des Bremsträgers ist zumindest ein Führungsbolzen zur axial verschiebbaren Lagerung des Bremsgehäuses unmittelbar an der in Umfangsrichtung elastisch nachgiebigen inneren Belagabstützung befestigt. Bei einer vorteilhaften Variante mit zwei Führungsbolzen an in Umfangsrichtung beiden Belagabstützungen folgen die Führungbolzen bei Bremseneingriff durch Parallelverschiebung in Umfangsrichtung gleichsam der Verformung der Bremstragerarme bzw. insbesondere der Verformung im Bereich der axial inneren Belagabstützung und verhindern somit eine Schiefstellung des Bremsgehäuses . Ein Ausführungsbeispiel der Erfindung wird anhand der Zeichnung dargestellt und im folgenden näher erläutert.In a further development of the brake carrier, 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. In an advantageous variant with two guide pins on both lining supports 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. An embodiment of the invention is illustrated by the drawing and explained in more detail below.
Es zeigen:Show it:
Fig. 1 eine dreidimensionale Rückansicht eines Bremsträgers mit in Umfangsrichtung elastischer Belagabstützung des inneren Bremsbelages,1 is a three-dimensional rear view of a brake carrier with circumferentially elastic pad support of the inner brake pad,
Fig. 2 eine dreidimensionale Draufsicht des Bremsträgers aus Fig. 1.FIG. 2 shows a three-dimensional top view of the brake carrier from FIG. 1.
Der in den Fig. 1 und 2 dargestellte Bremsträger 1 einer Teilbelagscheibenbremse besteht im wesentlichen aus einem sich in einer Sekantenrichtung der nicht gezeigten Bremsscheibe erstreckenden Basisabschnitt 2 sowie zwei sich an die seitlichen Enden des Basisabschnitts 2 anschließenden Bremstragerarmen 3 , die in axialer Richtung den äußeren Rand einer nicht gezeigten Bremsscheibe überragen. Der Basisabschnitt 2 ist über zwei Durchgangslöcher 4 insbesondere am Achsschenkel eines Kraftfahrzeuges zu verschraubbar . Die im Abstand voneinander angeordneten parallelen Bremstragerarme 3 sind einstückig mit dem Basisabschnitt 2 verbunden und dienen zur axial verschiebbaren Führung und Abstützung nicht gezeigter Bremsbeläge. Dazu sind in den Bremstragerarmen 3 jeweils axiale Führungsnuten 5 ausgebildet, die in radialer Richtung nach außen geöffnet sind. Die nicht gezeigten Bremsbeläge greifen mit hakenförmigen, seitlichen Tragteilen in die Führungsnuten 5 ein und ermöglichen damit die an den Bremsbelägen in Umfangsrichtung auftretende Reibungskraft auf beide Bremstragerarme 3 zu übertragen. Im einzelnen wird dies durch senkrecht zur Umfangsrichtung orientierte Abstützflachen 6 innerhalb der Führungsnuten 5 realisiert. Die der Bremsenmitte zu- bzw. abgewandten Abstützflachen 6 bewirken zusammen mit entsprechend orientierten Anlageflächen an den nicht ge- zeigten Bremsbelägen eine ziehende (Pull) und/oder drückende (Push) Abstützung der beiden Bremsbeläge. Idealerweise wird durch gezielte Auslegung der Toleranzfelder für die Tragteile der Bremsbeläge bzw. die Führungsnuten 5 erreicht, daß bei den üblicherweise im Betrieb häufig auftretenden geringen Bremsanlagekräften, insbesondere bei Abbremsungen bis 30-50 %, eine einlaufseitig ziehende Abstützung beider Bremsbeläge eingestellt wird. Erst bei größeren Bremsanlegekräften und der Übertragung höherer Bremsleistungen erfolgt eine Push- Pull-Abstützung beider Bremsbeläge und damit die Übertragung der Reibungskräfte auf beide Bremstragerarme 3. Die Sicherstellung der Push-Pull-Abstützung beider Bremsbeläge im Falle hoher Bremsbetätigungskräfte wird durch eine in Umfangsrichtung elastisch nachgiebige Ausbildung der Bremsbelagabstüt- zungen an den Bremstragerarmen 3 gewährleistet. Die Belagabstützung 7 für den axial äußeren Bremsbelag unterliegt aufgrund der Hebelarme des Bremsträgerarmes 3 ohnehin einer gewissen Elastizität. Um eine gleichartige in Umfangsrichtung elastische Abstützung auch für den axial inneren Bremsbelag zu gewährleisten, ist die axial innere Belagabstützung 8 an einem im wesentlichen axial verlaufenden Steg 9 ausgebildet. Der Steg 9 ist einstückig mit dem Bremsträgerarm 3 verbunden und weist bei Belastung eine elastische Nachgiebigkeit in radialer wie auch in tangentialer Richtung auf. In Umfangsrichtung verbleibt zwischen dem Steg 9 und dem Bremsträgerarm 3 eine axial sich erstreckende Ausnehmung 10.1 and 2 of 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. For this purpose, 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, not shown, 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. In particular, 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. Ideally, through targeted design of the tolerance fields for the supporting parts of the brake pads or the guide grooves 5, it is achieved that, in the case of the low brake system forces that commonly occur during operation, in particular in the case of decelerations of up to 30-50%, support on both sides of the brake pads is set. Only with larger brake application forces and the transmission of higher braking powers is there a push-pull support of both brake pads and thus the transmission of the frictional forces to both brake support arms 3. The push-pull support of both brake pads is ensured in the case of high brake actuation forces by an elastically flexible in the circumferential direction Training of the brake pad supports on the brake support arms 3 guaranteed. 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. In order to ensure a similar support in the circumferential direction also for the axially inner brake pad, 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.
Im Unterschied zu bisher bekannten Bremsträgern 1, bei denen die innere Belagabstützung 8 häufig massiv an den Bremsträgerarm 3 bzw. den Basisabschnitt 2 angebunden ist, läßt sich die innere Belagabstützung 8 beim Bremsträger 1 aus Fig. 1 erheblich leichter in Umfangsrichtung elastisch verformen. Die unvermeidliche Verformung insbesondere der Bremstragerarme 3 bei bekannten Bremsträgerausführungen äußerte sich insbesondere in einer Schiefstellung der Bremstragerarme 3 in Drehrichtung der Bremsscheibe. Eine solche Schiefstellung wirkt sich in Form einer Tangentialverschiebung sehr stark auf die axial äußeren Belagabstützungen 7 aus. Bei dem in den Figuren dargestellten erfindungsgemäßen Bremsträger 1 kann durch gezielte konstruktive Auslegung des Steges 9 sowie der Ausnehmung 10 die elastische Nachgiebigkeit in Umfangsrichtung der inneren Belagabstützung 8 an die der äußeren Belagabstützung 7 angepaßt werden. Dadurch kann ein unerwünschter Schrägverschleiß an den Bremsbelägen und eine daraus resultierende stärkere Tendenz zu Bremsgeräuschen für verschiedenste Bremsentypen mit gattungsgemäßen Bremsträgern vermieden werden. Desweiteren kann dadurch die bewußte Push-Pull-Aus- legung beider Bremsbeläge bei Teilbelagscheiben dieses Bremsentyps erleichtert werden.In contrast to previously known brake carriers 1, in which the inner lining support 8 is often massively connected to the brake carrier arm 3 or the base section 2, 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. In the brake carrier 1 according to the invention shown in the figures, 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. As a result, 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. Furthermore, the deliberate push-pull design of both brake linings can be facilitated in the case of partial brake pads of this type of brake.
Eine weiterer Vorteil ergibt sich daraus, die am Bremsträger 1 befestigten, nicht gezeigten Führungsbolzen in unmittelbarer Nähe der in Umfangsrichtung elastischen inneren Belagabstützung 8 am Bremsträger 1 anzuordnen. Üblicherweise werden dabei zwei Führungsbolzen in Gewindebohrungen 11 von Befestigungsaugen 12 am Basisabschnitt 2 eingeschraubt. Die im Abstand voneinander axial orientierten Führungsbolzen sind innerhalb von Bohrungen des nicht gezeigten Bremsgehäuses axial verschiebbar gelagert. Die Anordnung der Befestigungsaugen 12 für die Führungsbolzen unmittelbar an der inneren Belagabstützung 8 resultiert in einer erheblichen Reduzierung der Schiefstellung des Bremsgehäuses bei Aufnahme hoher Bremsumfangskräfte durch den Bremsträger 1. Bei derartig hohen Bremsumfangskräften folgen die Befestigungsaugen 12 unter Beibehaltung ihrer parallelen, axialen Ausrichtung der elastischen Verformung der am Steg 9 ausgebildeten inneren Belagabstützung 8 sowohl einlauf- als auch auslaufseitig. Es ergibt sich damit im wesentlichen eine Parallelverschiebung der inneren wie auch der äußeren Belagabstützung sowie der beiden Befestigungsaugen 12 mit den Führungsbolzen in Dreh- richtung der nicht gezeigten Bremsscheibe. Eine mögliche Schiefstellung der Bremstragerarme 3 bzw. eine Schiefstellung des Bremsgehäuses kann dadurch erfolgreich vermieden bzw. in ganz erheblichem Maß reduziert werden.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. Usually, 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. With such high braking peripheral forces, the fastening eyes 12 follow the elastic deformation while maintaining their parallel, axial orientation the inner lining support 8 formed on the web 9 both on the inlet and outlet side. This essentially results in a parallel displacement of the inner as well as the outer lining support as well as the two fastening eyes 12 with the guide bolts in rotational direction of the brake disc, not shown. A possible skewing of the brake support arms 3 or a skewing of the brake housing can thereby be successfully avoided or reduced to a very considerable extent.
In einfachster Weise wird die Ausführung des Steges 9 bzw. der Ausnehmung 10 unmittelbar bei der Ausgestaltung des durch Guß hergestellten Bremsträgerrohlings 1 angeformt. Dadurch werden zusätzliche spanende Bearbeitungsgänge vermieden. An den grundsätzlichen Abmessungen des Bremsträgers 1 wird durch die erfindungsgemäßen konstruktiven Maßnahmen zunächst nichts geändert. Die bestehenden Bearbeitungsgänge am gegossenen Rohteil können dabei unter Einsatz vorhandener Werkzeuge bzw. Maschinen beibehalten werden.In the simplest manner, 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.
Die Ausgestaltung der in Umfangsrichtung gleichen elastischen Abstützung für den inneren wie auch den äußeren Bremsbelag ist selbstverständlich nicht auf das in den Figuren dargestellte Ausführungsbeispiel beschränkt. Die Herabsetzung der Materialsteifigkeit der inneren Belagabstützung 8 läßt sich je nach Art der gewählten Belagabstützung durchaus auch ausschließlich am einlauf- bzw. auslaufseitigen Bremsträgerarm 3 realisieren. Damit läßt sich das Prinzip bei jeder Art der Belagabstützung umsetzen. 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.

Claims

Patentansprüche claims
1. Bremsträger (1) für eine Teilbelagscheibenbremse, mit einem eine Bremsscheibe und beiderseits der Bremsscheibe angeordnete Bremsbeläge umgreifenden Bremsgehäuse, das axial verschiebbar am Bremsträger (1) gelagert ist und auf der axial inneren Bremsscheibenseite eine hydraulische Betätigungsvorrichtung besitzt, mit der der axial innere Bremsbelag direkt und der axial äußere Bremsbelag durch Axialverschiebung des Bremsgehäuses indirekt mit der Bremsscheibe in Anlage bringbar ist, wobei der Bremsträger (1) ausgehend von einem Basisabschnitt (2) zwei axial die Bremsscheibe übergreifende Bremstragerarme (3) aufweist, an denen die Bremsbeläge axial verschiebbar geführt und abgestützt sind, dadurch gekennzeichnet, daß zumindest einseitig an der Belagabstützung (8) des inneren Bremsbelages die Materialsteifigkeit des Bremsträgerarmes (3) in Umfangsrichtung gezielt herabgesetzt ist, um für den inneren und den äußeren Bremsbelag eine in Umfangsrichtung annähernd gleiche elastische Abstützung am Bremsträgeram (3) zu erreichen.1.Brake carrier (1) for a partial brake disc brake, with a brake housing encompassing a brake disc and brake linings arranged on both sides of the brake disc, which is axially displaceably mounted on the brake carrier (1) and has a hydraulic actuating device on the axially inner brake disc side with which the axially inner brake lining directly and the axially outer brake pad can be brought into direct contact with the brake disc by axially displacing the brake housing, the brake carrier (1), starting from a base section (2), having two brake support arms (3) axially overlapping the brake disc, on which the brake pads are axially displaceably guided and are supported, characterized in that at least on one side on the lining support (8) of the inner brake lining, the material rigidity of the brake support arm (3) is reduced in the circumferential direction in order to achieve an approximately equal e in the circumferential direction for the inner and outer brake lining to achieve elastic support on the brake carrier at (3).
2. Bremsträger (1) nach Anspruch 1, dadurch gekennzeichnet, daß die Bremsbeläge in Umfangsrichtung derart formschlüssig an den Bremstragerarmen (3) abgestützt sind, daß zumindest bei höheren Bremsanlegekräften die an den Bremsbelägen in Umfangsrichtung auftretende Reibungskraft auf beide Bremstragerarme (3) übertragen wird.2. Brake carrier (1) according to claim 1, characterized in that the brake pads are supported in the circumferential direction in such a form-fitting manner on the brake support arms (3) that at least with higher brake application forces, the frictional force occurring on the brake pads in the circumferential direction is transmitted to both brake support arms (3) .
3. Bremsträger (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß zumindest ein Bremsträgerarm (3) an der in Umfangsrichtung der Symmetrieebene der Teilbelagscheibenbremse abgewandten Seite der axial inneren Belagabstützung (8) eine axial sich erstreckende Ausnehmung (10) aufweist. 3. Brake carrier (1) according to one of the preceding claims, characterized in that at least one brake carrier arm (3) on the side facing away from the axially inner lining support (8) in the circumferential direction of the plane of symmetry of the partial brake disc brake has an axially extending recess (10).
4. Bremsträger nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die mit der axial äußeren Belagabstützung (7) fluchtende axial innere Belagabstützung (8) zumindest einseitig an einem im wesentlichen axial verlaufenden, einstückig mit dem Bremsträgerarm (3) verbundenen Steg (9) ausgebildet ist.4. Brake carrier according to one of the preceding claims, characterized in that the axially outer lining support (7) aligned axially inner lining support (8) at least on one side on a substantially axially extending, integrally connected to the brake carrier arm (3) web (9) is trained.
5. Bremsträger (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Bremsträgerrohling durch Gießen hergestellt ist.5. Brake carrier (1) according to one of the preceding claims, characterized in that the brake carrier blank is produced by casting.
6. Bremsträger nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Bremsträger (1) zumindest einen am Bremsträger (1) befestigten Führungsbolzen aufweist, der innerhalb einer Bohrung des Bremsgehäuses axial verschiebbar geführt ist.6. Brake carrier according to one of the preceding claims, characterized in that the brake carrier (1) has at least one guide bolt attached to the brake carrier (1) which is guided axially displaceably within a bore of the brake housing.
7. Bremsträger (1) nach Anspruch 6, dadurch gekennzeichnet, daß der Führungsbolzen unmittelbar an der inneren Belagabstützung (8) am Bremsträger (1) befestigt ist. 7. brake carrier (1) according to claim 6, characterized in that the guide pin is attached directly to the inner pad support (8) on the brake carrier (1).
PCT/EP1997/006303 1996-12-05 1997-11-12 Brake carrier for a partially lined disc brake WO1998025044A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP52511398A JP2001509233A (en) 1996-12-05 1997-11-12 Brake support for spot type disc brakes
EP97951888A EP0941418A1 (en) 1996-12-05 1997-11-12 Brake carrier for a partially lined disc brake

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1996150425 DE19650425B4 (en) 1996-12-05 1996-12-05 Brake carrier for a partial lining disc brake
DE19650425.2 1996-12-05

Publications (1)

Publication Number Publication Date
WO1998025044A1 true WO1998025044A1 (en) 1998-06-11

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ID=7813704

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Application Number Title Priority Date Filing Date
PCT/EP1997/006303 WO1998025044A1 (en) 1996-12-05 1997-11-12 Brake carrier for a partially lined disc brake

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EP (1) EP0941418A1 (en)
JP (1) JP2001509233A (en)
DE (1) DE19650425B4 (en)
WO (1) WO1998025044A1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10004182A1 (en) * 2000-02-01 2001-08-02 Continental Teves Ag & Co Ohg Disc brake for motor vehicle has break in bridge connecting brake lining support to brake support arm and is broken in region of inner brake lining
DE10314437A1 (en) * 2003-03-31 2004-10-14 Continental Teves Ag & Co. Ohg Brake carrier for a partial brake disc brake
DE10358086A1 (en) * 2003-12-10 2005-07-14 Continental Teves Ag & Co. Ohg Partially lined disk brake for a motor vehicle comprises a brake anchor plate designed so that the flexibility of a support for an outer brake pad on the side facing away from a piston is reduced by a piston-side strut
CN101947592B (en) * 2010-08-24 2012-10-24 包头北方创业股份有限公司 Brake beam stretching anti-cracking device
DE102016104967A1 (en) 2015-10-09 2017-04-13 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH brake carrier

Citations (5)

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Publication number Priority date Publication date Assignee Title
DE2804808A1 (en) * 1978-02-04 1979-08-09 Teves Gmbh Alfred BRAKE SHOE BRACKET FOR A PARTING DISC BRAKE, ESPECIALLY FOR MOTOR VEHICLES
GB2014675A (en) * 1978-02-16 1979-08-30 Nissan Motor Disc Brake Assembly
EP0350867A1 (en) * 1988-07-15 1990-01-17 LUCAS INDUSTRIES public limited company Spot-type disc brake
EP0359548A1 (en) * 1988-09-14 1990-03-21 Pbr Automotive Pty Ltd Floating caliper disc brake
DE4431724A1 (en) 1994-09-06 1996-03-07 Teves Gmbh Alfred Disc brake caliper with pad telltale

Family Cites Families (1)

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Publication number Priority date Publication date Assignee Title
DE3913904A1 (en) * 1989-04-27 1990-10-31 Teves Gmbh Alfred Floating saddle disc brake - especially for vehicles with brake support, has brake shoes, with lining back plate, saddle and brake disc with two arms

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2804808A1 (en) * 1978-02-04 1979-08-09 Teves Gmbh Alfred BRAKE SHOE BRACKET FOR A PARTING DISC BRAKE, ESPECIALLY FOR MOTOR VEHICLES
GB2014675A (en) * 1978-02-16 1979-08-30 Nissan Motor Disc Brake Assembly
EP0350867A1 (en) * 1988-07-15 1990-01-17 LUCAS INDUSTRIES public limited company Spot-type disc brake
EP0359548A1 (en) * 1988-09-14 1990-03-21 Pbr Automotive Pty Ltd Floating caliper disc brake
DE4431724A1 (en) 1994-09-06 1996-03-07 Teves Gmbh Alfred Disc brake caliper with pad telltale

Also Published As

Publication number Publication date
DE19650425A1 (en) 1998-06-10
EP0941418A1 (en) 1999-09-15
JP2001509233A (en) 2001-07-10
DE19650425B4 (en) 2007-04-05

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