EP2404075A1 - Brake disk - Google Patents

Brake disk

Info

Publication number
EP2404075A1
EP2404075A1 EP10706920A EP10706920A EP2404075A1 EP 2404075 A1 EP2404075 A1 EP 2404075A1 EP 10706920 A EP10706920 A EP 10706920A EP 10706920 A EP10706920 A EP 10706920A EP 2404075 A1 EP2404075 A1 EP 2404075A1
Authority
EP
European Patent Office
Prior art keywords
brake disc
friction ring
hub
brake disk
brake
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Withdrawn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
EP10706920A
Other languages
German (de)
French (fr)
Inventor
Matthias Mitschang
Ralph Mayer
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.)
Mercedes Benz Group AG
Original Assignee
Daimler AG
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 Daimler AG filed Critical Daimler AG
Publication of EP2404075A1 publication Critical patent/EP2404075A1/en
Withdrawn legal-status Critical Current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
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/12—Discs; Drums for disc brakes
    • F16D65/123—Discs; Drums for disc brakes comprising an annular disc secured to a hub member; Discs characterised by means for mounting
    • 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
    • F16D2065/1304—Structure
    • F16D2065/1316—Structure radially segmented
    • 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
    • F16D2065/1356—Connection interlocking
    • F16D2065/136—Connection interlocking with relative movement radially
    • 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

Definitions

  • the invention relates to a brake disk for a motor vehicle according to the preamble of patent claim 1.
  • So-called composite brake discs so brake discs whose friction ring and brake disc hub made of different materials are well known. Such is disclosed for example in DE 198 30 666 A1.
  • Composite brake discs are increasingly being used, since the separation of the brake disc hub and the friction ring makes it possible, in each case, to optimize the aforementioned parts for their use.
  • DE 198 30 666 A1 teaches to provide a profile on an inner circumference of the friction ring and to press the brake disk hub to this profile by hydroforming.
  • the hydroforming is a complex process, which is associated with relatively high production costs. Since the hydroforming of the brake disk hub creates a play-free seating of the friction ring on the brake disk chamber both in the radial and in the axial direction, such brake disks are still associated with the disadvantage that there is no scope for compensating for different thermal expansion of the friction ring and brake disk chamber.
  • a brake disc according to the preamble of claim 1 further develop so that their production is simplified and greater design freedom in the design of the axial and radial securing of brake disk pot against friction ring are opened.
  • Such a brake disk has a brake disk pot and a friction ring disposed coaxially therewith, wherein an outer lateral surface of the brake disk pot has a profile which engages in a complementary profile of an inner circumferential surface of the friction ring for torque transmission. Furthermore, an axial securing of the friction ring relative to the brake disk chamber is provided. According to the invention, this axial securing is provided by at least one tab on the outer circumferential surface of the brake disk hub.
  • the profile of the brake disk hub thus assumes only the function of the radial securing, ie the torque transmission between the brake disk chamber and the friction ring.
  • the axial securing is performed by a separate element, namely a tab.
  • no additional fasteners are needed to keep the friction ring secured to the brake disc chamber in the axial direction. This simplifies the manufacture of the brake disc and thereby saves costs.
  • the tab for axial securing from the wall of the brake disc hub is punched out and bent. This can advantageously be done in a single step with a suitable tool, so that a particularly simple production of the brake disc according to the invention is made possible.
  • the tab may alternatively engage in an opening of the friction ring or abut a surface of the friction ring.
  • an axially oriented stopper can also fulfill an enforcement, which can also be realized in one work step. As a result, if required, higher axial forces than with radially shaped tabs can be supported.
  • At least one radially projecting retaining element is formed on one edge of the outer circumferential surface of the brake disk hub, which bears against an end face of the friction ring. This ensures additional securing of the friction ring in the axial direction, again requiring no additional connecting elements.
  • tab on the outer lateral surface of this holding element can be produced by a simple, one-step forming process.
  • the profiles of the friction ring and the brake disk chamber are designed as toothing. This allows a particularly good and low-load torque transmission between the brake disk hub and friction ring.
  • the possibility of axial expansion also offers a holding element, which rests only partially on the friction ring and in the intermediate region a distance in the order of the thermal friction ring extension or the
  • Axialverschiebungs cassettes has. This ensures an elastic-plastic character of the stop.
  • tab and retaining element results in a particularly precise geometric positioning between the brake disc and the friction ring, which reduces the unwanted flattening of the brake disc.
  • the axial displaceability between the two components is preferably prevented by an excess of the brake disk hub.
  • a flank angle of the toothing of the brake disk hub is 55 ° to 65 °.
  • the toothing is preferably formed asymmetrically, with a gap width of the toothing of the friction ring 4.5 to 6 mm and a gap width of the toothing of the brake disc hub is 7.5 to 9.5 mm.
  • the brake disk pot is preferably made of steel. In this case, electrochemical corrosion is advantageously avoided in the connection of the brake disk hub with a friction ring made of cast iron.
  • the invention further relates to a motor vehicle with a brake disc of the type described.
  • Fig. 1 is a perspective view of an embodiment of a brake disc according to the invention
  • Fig. 2 is a detail view of the axial and radial securing elements of such a brake disc and
  • Fig. 3 is a sectional view through the toothing between the brake disk hub and friction ring of an embodiment of a brake disc according to the invention.
  • FIGS. 4A and B show a detailed view of the axial and radial securing elements of such a brake disc in an alternative embodiment.
  • a designated as a whole with 10 brake disc comprises a brake disc hub 12 and a friction ring 14.
  • the friction ring has two friction surfaces 16, 18 which come in operation of the brake in tribological contact with the brake shoes. Due to the particularly good frictional properties such friction rings 14 are usually made of cast iron, in particular gray cast iron.
  • the friction ring 14 is designed as an internally ventilated friction ring and consists of two friction ring halves 20, 22 which are interconnected via connecting knobs 24, which are not all designated for clarity. As a result, 26 channels 26 are formed between the friction ring halves 20, through which ambient air can flow and thus dissipate heat.
  • each channels 28 are introduced, which open into the channels 26 and on the friction surfaces 16, 18 exit to further improve the air flow of the friction ring 14.
  • the brake disk cup 12 has an end face 30, into which openings 32, 34 are inserted, so as to connect the brake disk cup with a hub. Furthermore, the brake disk cup 12 has a jacket wall 38, via which the brake disk cup 12 is connected to the friction ring 14. Since no requirements are made with respect to its friction properties to the brake disk hub 12, this can be carried out to save weight instead of cast iron from sheet metal, such as steel.
  • the casing wall 38 of the brake disk cup 12 has a tooth profile which engages in a complementary profile of an inner casing wall 40 of the friction ring 12.
  • a radial securing of the friction ring 14 with respect to the brake disk hub 12 is achieved, so that torques between the two parts 12, 14 can be transmitted.
  • tabs 42 are punched out of the casing wall 38, which engage in complementary openings of the friction ring 14, which can not be seen in the drawing.
  • a further axial securing is produced by holding elements 44, which project radially outward at the edge 46 of the jacket wall 38 and bear against the inner surface 48 of the friction ring half 22.
  • the tabs 42 can not engage in receiving openings of the friction ring half 22, but rather abut against the friction surface 18 of the second friction ring half 22. Due to the respective distances between tabs 42 and retaining elements 44, a floating mounting of the friction ring 14 on the brake disk hub 12 can be achieved, so that a certain amount of play remains in the axial direction. Thus, for example, different thermal expansions of the friction ring 14 and the brake disk hub 12 can be compensated.
  • the toothing between the friction ring 14 and the brake disk hub 12 is formed asymmetrically, wherein the teeth 50 of the brake disk hub 12 are made narrower than the teeth 52 of the friction ring 14.
  • the gap width d1 of the toothing of the friction ring 14 is 4, 5 to 6 mm, the gap width d2 of the teeth of the brake disk hub 12 7.5 to 9.5 mm.
  • the flank angle ⁇ of the teeth of the brake disk hub is between 55 ° and 65 °.
  • Such an asymmetrical and closely meshed toothing of the brake disk cup 12 and the friction ring 14 achieves a particularly good and low-wear torque transmission between the brake disk cup 12 and the friction ring 14.
  • 4A and B show an alternative embodiment in which a tab 52 engages around the edge of the jacket wall of the brake disk hub, the friction ring, wherein a counter-lock is provided by a stop 54.

Landscapes

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

Abstract

The invention relates to a brake disk (10) for a motor vehicle, having a brake disk chamber (12) and a friction ring (14) coaxially disposed thereto, wherein an external lateral surface (38) of the brake disk chamber has a profile which engages a complementary profile of an internal lateral surface (40) of the friction ring (14) for transmitting torque, and wherein the friction ring (14) is disposed in an axially secured manner at the brake disk chamber (12), wherein at least one strap (42) for axially securing same is formed at the external lateral surface (38) of the brake disk chamber (12).

Description

Bremsscheibe brake disc
Die Erfindung betrifft eine Bremsscheibe für einen Kraftwagen nach dem Oberbegriff von Patentanspruch 1.The invention relates to a brake disk for a motor vehicle according to the preamble of patent claim 1.
So genannte Verbundbremsscheiben, also Bremsscheiben, deren Reibring und Bremsscheibentopf aus unterschiedlichen Materialien bestehen, sind allgemein bekannt. Eine solche ist beispielsweise in der DE 198 30 666 A1 offenbart. Verbundbremsscheiben finden zunehmend Verwendung, da durch die Trennung von Bremsscheibentopf und Reibring die genannten Teile jeweils für sich genommen für ihren Einsatz optimiert werden können. So ist es beispielsweise möglich, Reibringe aus Gusseisen, welches hervorragende tribologische und Wärmeleiteigenschaften aufweist, mit Bremsscheibentöpfen aus Blech zu kombinieren, um so die gesamte Bremsscheibe leichter zu gestalten und damit die ungefederte Masse eines Kraftwagens mit einer solchen Bremsscheibe zu verringern.So-called composite brake discs, so brake discs whose friction ring and brake disc hub made of different materials are well known. Such is disclosed for example in DE 198 30 666 A1. Composite brake discs are increasingly being used, since the separation of the brake disc hub and the friction ring makes it possible, in each case, to optimize the aforementioned parts for their use. Thus, for example, it is possible to combine friction rings made of cast iron, which has excellent tribological and thermal conduction properties, with brake disk pots made of sheet metal, so as to make the entire brake disk lighter and thus to reduce the unsprung mass of a motor vehicle with such a brake disc.
Um den Bremsscheibentopf an den Reibring zu fügen, lehrt die DE 198 30 666 A1 ein Profil an einem Innenumfang des Reibrings vorzusehen und den Bremsscheibentopf durch Innenhochdruckumformen an dieses Profil anzupressen.In order to attach the brake disk hub to the friction ring, DE 198 30 666 A1 teaches to provide a profile on an inner circumference of the friction ring and to press the brake disk hub to this profile by hydroforming.
Nachteiligerweise ist das Innenhochdruckumformen ein aufwändiger Prozess, der mit relativ hohen Herstellungskosten verbunden ist. Da durch das Innenhochdruckumformen des Bremsscheibentopfes ein spielfreier Sitz des Reibringes am Bremsscheibentopf sowohl in radialer als auch in axialer Richtung entsteht, sind derart gefügte Bremsscheiben weiterhin mit dem Nachteil behaftet, dass kein Spielraum zur Kompensation von unterschiedlicher Wärmeausdehnung von Reibring und Bremsscheibentopf besteht.Disadvantageously, the hydroforming is a complex process, which is associated with relatively high production costs. Since the hydroforming of the brake disk hub creates a play-free seating of the friction ring on the brake disk chamber both in the radial and in the axial direction, such brake disks are still associated with the disadvantage that there is no scope for compensating for different thermal expansion of the friction ring and brake disk chamber.
Der vorliegenden Erfindung liegt somit die Aufgabe zugrunde, eine Bremsscheibe nach dem Oberbegriff von Patentanspruch 1 so weiterzuentwickeln, dass ihre Herstellung vereinfacht wird und größere konstruktive Spielräume bei der Ausgestaltung von axialer und radialer Sicherung von Bremsscheibentopf gegen Reibring eröffnet werden.The present invention is therefore based on the object, a brake disc according to the preamble of claim 1 further develop so that their production is simplified and greater design freedom in the design of the axial and radial securing of brake disk pot against friction ring are opened.
Diese Aufgabe wird durch eine Bremsscheibe mit den Merkmalen von Patentanspruch 1 gelöst.This object is achieved by a brake disc with the features of claim 1.
Eine solche Bremsscheibe weist einen Bremsscheibentopf und einen zu diesem koaxial angeordneten Reibring auf, wobei eine äußere Mantelfläche des Bremsscheibentopfes ein Profil aufweist, welches zur Drehmomentübertragung in ein komplementäres Profil einer inneren Mantelfläche des Reibrings eingreift. Weiterhin ist eine axiale Sicherung des Reibringes gegenüber dem Bremsscheibentopf vorgesehen. Erfindungsgemäß wird diese axiale Sicherung durch wenigstens eine Lasche an der äußeren Mantelfläche des Bremsscheibentopfes bereitgestellt.Such a brake disk has a brake disk pot and a friction ring disposed coaxially therewith, wherein an outer lateral surface of the brake disk pot has a profile which engages in a complementary profile of an inner circumferential surface of the friction ring for torque transmission. Furthermore, an axial securing of the friction ring relative to the brake disk chamber is provided. According to the invention, this axial securing is provided by at least one tab on the outer circumferential surface of the brake disk hub.
Im Gegensatz zum Stand der Technik übernimmt das Profil des Bremsscheibentopfes somit nur die Funktion der radialen Sicherung, also der Drehmomentübertragung zwischen Bremsscheibentopf und Reibring. Die axiale Sicherung wird durch ein getrenntes Element, nämlich eine Lasche ausgeführt. Im Gegensatz zu anderen bekannten Methoden der axialen Sicherung - wie beispielsweise Nieten, Bolzen, Schrauben - sind keine zusätzlichen Verbindungselemente nötig, um den Reibring am Bremsscheibentopf in axialer Richtung gesichert zu halten. Dies vereinfacht die Herstellung der Bremsscheibe und spart dadurch Kosten ein.In contrast to the prior art, the profile of the brake disk hub thus assumes only the function of the radial securing, ie the torque transmission between the brake disk chamber and the friction ring. The axial securing is performed by a separate element, namely a tab. In contrast to other known methods of axial securing - such as rivets, bolts, screws - no additional fasteners are needed to keep the friction ring secured to the brake disc chamber in the axial direction. This simplifies the manufacture of the brake disc and thereby saves costs.
In einer weiteren Ausführungsform kann ebenso auf Zusatzelemente zur axial gerichteten Sicherung verzichtet werden, indem der Topf gegenüber dem Reibring mit einem im Temperaturgebiet beim Bremsen ausreichend dimensionierten Übermaß gefügt wird.In a further embodiment can also be dispensed with additional elements for axially directed fuse by the pot relative to the friction ring is added with a sufficiently dimensioned in the temperature range during braking oversize.
In einer bevorzugten Ausführungsform der Erfindung ist die Lasche zur axialen Sicherung aus der Wandung des Bremsscheibentopfes ausgestanzt und umgebogen. Dies kann vorteilhafterweise in einem einzigen Arbeitsschritt mit einem geeigneten Werkzeug erfolgen, so dass eine besonders einfache Herstellung der erfindungsgemäßen Bremsscheibe ermöglicht ist.In a preferred embodiment of the invention, the tab for axial securing from the wall of the brake disc hub is punched out and bent. This can advantageously be done in a single step with a suitable tool, so that a particularly simple production of the brake disc according to the invention is made possible.
Die Lasche kann alternativ in eine Öffnung des Reibringes eingreifen oder an einer Fläche des Reibringes anliegen. Es besteht somit die konstruktive Freiheit bei der Axialsicherung des Reibringes gegenüber dem Bremsscheibentopf auch ein gewisses Spiel vorzusehen, also eine zumindest teilweise schwimmende Lagerung zu realisieren. Dadurch können beispielsweise unterschiedliche Wärmeausdehnungen von Reibring und Bremsscheibentopf in dessen Betrieb kompensiert werden.The tab may alternatively engage in an opening of the friction ring or abut a surface of the friction ring. Thus, there is the constructive freedom in the axial securing of the friction ring relative to the brake disk chamber also to provide a certain clearance, that is to realize an at least partially floating mounting. Thereby can For example, different thermal expansions of friction ring and brake disk pot can be compensated in its operation.
Alternativ kann die Funktion eines axial orientierten Anschlags auch eine Durchsetzung erfüllen, welche ebenso in einem Arbeitsschritt realisierbar ist. Dadurch können bei Bedarf auch höhere Axialkräfte als bei radial ausgeformten Laschen abgestützt werden.Alternatively, the function of an axially oriented stopper can also fulfill an enforcement, which can also be realized in one work step. As a result, if required, higher axial forces than with radially shaped tabs can be supported.
In einer weiteren bevorzugten Ausführungsform der Erfindung ist an einer Kante der äußeren Mantelfläche des Bremsscheibentopfes wenigstens ein radial abragendes Halteelement ausgebildet, welches an einer Stirnfläche des Reibrings anliegt. Damit wird eine zusätzliche Sicherung des Reibringes in axialer Richtung gewährleistet, wobei wiederum keine zusätzlichen Verbindungselemente notwendig sind. Genau wie die bereits geschilderte Lasche an der äußeren Mantelfläche kann dieses Halteelement durch einen einfachen, einschrittigen Umformprozess erzeugt werden.In a further preferred embodiment of the invention, at least one radially projecting retaining element is formed on one edge of the outer circumferential surface of the brake disk hub, which bears against an end face of the friction ring. This ensures additional securing of the friction ring in the axial direction, again requiring no additional connecting elements. Just like the previously described tab on the outer lateral surface of this holding element can be produced by a simple, one-step forming process.
In einer weiteren Ausführungsform sind die Profile von Reibring und Bremsscheibentopf als Verzahnung ausgebildet. Dies ermöglicht eine besonders gute und belastungsarme Drehmomentübertragung zwischen Bremsscheibentopf und Reibring.In a further embodiment, the profiles of the friction ring and the brake disk chamber are designed as toothing. This allows a particularly good and low-load torque transmission between the brake disk hub and friction ring.
Die Möglichkeit der axialen Ausdehnung bietet darüber hinaus ein Halteelement, das lediglich teilweise am Reibring anliegt und im Zwischenbereich einen Abstand in Größenordnung der thermischen Reibringausdehnung bzw. desThe possibility of axial expansion also offers a holding element, which rests only partially on the friction ring and in the intermediate region a distance in the order of the thermal friction ring extension or the
Axialverschiebungsbedarfs aufweist. Dadurch ist ein elastisch-plastischer Charakter des Anschlags gewährleistet. In der Kombination von Lasche und Halteelement ergibt sich eine besonders präzise geometrische Positionierung zwischen Bremsscheibe und Reibring, welche den unerwünschten Planschlag der Bremsscheibe vermindert. Die axiale Verschiebbarkeit zwischen den beiden Bauteilen wird hierbei bevorzugt durch ein Übermaß des Bremsscheibentopfes verhindert.Axialverschiebungsbedarfs has. This ensures an elastic-plastic character of the stop. In the combination of tab and retaining element results in a particularly precise geometric positioning between the brake disc and the friction ring, which reduces the unwanted flattening of the brake disc. The axial displaceability between the two components is preferably prevented by an excess of the brake disk hub.
Bevorzugt beträgt ein Flankenwinkel der Verzahnung des Bremsscheibentopfes 55° bis 65°. Die Verzahnung ist dabei bevorzugterweise asymmetrisch ausgebildet, wobei eine Lückenweite der Verzahnung des Reibrings 4,5 bis 6 mm und eine Lückenweite der Verzahnung des Bremsscheibentopfes 7,5 bis 9,5 mm beträgt. Durch eine derartige engmaschige und asymmetrische Verzahnung kann besonders materialsparend eine Maximierung des Torsionswiderstandsmomentes zwischen Bremsscheibe und Reibring realisiert werden. Bevorzugterweise besteht der Bremsscheibentopf aus Stahl. Dabei wird vorteilhaft elektrochemische Korrosion bei der Verbindung des Bremsscheibentopfes mit einem Reibring aus Gusseisen vermieden.Preferably, a flank angle of the toothing of the brake disk hub is 55 ° to 65 °. The toothing is preferably formed asymmetrically, with a gap width of the toothing of the friction ring 4.5 to 6 mm and a gap width of the toothing of the brake disc hub is 7.5 to 9.5 mm. By means of such a close-meshed and asymmetrical toothing, maximizing the torsional resistance torque between the brake disk and the friction ring can be realized in a particularly material-saving manner. The brake disk pot is preferably made of steel. In this case, electrochemical corrosion is advantageously avoided in the connection of the brake disk hub with a friction ring made of cast iron.
Die Erfindung betrifft weiterhin einen Kraftwagen mit einer Bremsscheibe der beschriebenen Art.The invention further relates to a motor vehicle with a brake disc of the type described.
Im Folgenden soll die Erfindung und ihre Ausführungsformen anhand der Zeichnungen näher erläutert werden. Hierbei zeigen:In the following, the invention and its embodiments will be explained in more detail with reference to the drawings. Hereby show:
Fig. 1 eine perspektivische Ansicht eines Ausführungsbeispiels einer erfindungsgemäßen Bremsscheibe;Fig. 1 is a perspective view of an embodiment of a brake disc according to the invention;
Fig. 2 eine Detailansicht der axialen und radialen Sicherungselemente einer solchen Bremsscheibe undFig. 2 is a detail view of the axial and radial securing elements of such a brake disc and
Fig. 3 eine Schnittdarstellung durch die Verzahnung zwischen Bremsscheibentopf und Reibring eines Ausführungsbeispiels einer erfindungsgemäßen Bremsscheibe.Fig. 3 is a sectional view through the toothing between the brake disk hub and friction ring of an embodiment of a brake disc according to the invention.
Fig. 4A und B eine Detailansicht der axialen und radialen Sicherungselemente einer solchen Bremsscheibe in einer alternativen Ausführungsform.4A and B show a detailed view of the axial and radial securing elements of such a brake disc in an alternative embodiment.
Eine im Ganzen mit 10 bezeichnete Bremsscheibe umfasst einen Bremsscheibentopf 12 und einen Reibring 14. Der Reibring besitzt zwei Reibflächen 16, 18, welche im Betrieb der Bremse in tribologischen Kontakt mit den Bremsbacken kommen. Aufgrund der besonders guten Reibeigenschaften sind solche Reibringe 14 in der Regel aus Gusseisen, insbesondere Grauguss gefertigt. Um die im Bremsbetrieb auftretende Wärme abzuleiten, ist der Reibring 14 als innenbelüfteter Reibring ausgeführt und besteht aus zwei Reibringhälften 20, 22 welche über Verbindungsnoppen 24, die der Übersichtlichkeit halber nicht alle bezeichnet sind, miteinander verbunden sind. Dadurch bilden sich zwischen den Reibringhälften 20, 22 Kanäle 26 aus, durch die Umgebungsluft strömen kann und so Wärme abführen kann. Auch in den Reibringhälften 20, 22 sind jeweils Kanäle 28 eingebracht, welche in die Kanäle 26 münden und auf den Reibflächen 16, 18 austreten, um die Luftdurchströmung des Reibrings 14 weiter zu verbessern. Der Bremsscheibentopf 12 weist eine Stirnfläche 30 auf, in die Öffnungen 32, 34 eingebracht sind, um den Bremsscheibentopf so mit einer Nabe zu verbinden. Weiterhin besitzt der Bremsscheibentopf 12 eine Mantelwandung 38, über welchen der Bremsscheibentopf 12 mit dem Reibring 14 verbunden wird. Da an den Bremsscheibentopf 12 keine Anforderungen hinsichtlich seiner Reibeigenschaften gestellt sind, kann dieser zur Gewichtseinsparung anstelle aus Gusseisen aus Blech, beispielsweise Stahlblech ausgeführt sein. Um Bremsscheibentopf 12 und Reibring 14 gegeneinander zu sichern, weist die Mantelwandung 38 des Bremsscheibentopfes 12 ein Zahnprofil auf, welches in eine komplementäres Profil einer inneren Mantelwandung 40 des Reibringes 12 eingreift. Dadurch wird eine radiale Sicherung des Reibringes 14 gegenüber dem Bremsscheibentopf 12 erzielt, so dass Drehmomente zwischen den beiden Teilen 12, 14 übertragen werden können. Um eine axiale Sicherung zwischen Bremsscheibentopf 12 und Reibring 14 herzustellen sind aus der Mantelwandung 38 Laschen 42 ausgestanzt, welche in komplementäre Öffnungen des Reibringes 14, die in der Zeichnung nicht zu erkennen sind, eingreifen. Eine weitere axiale Sicherung wird durch Halteelemente 44 erzeugt, welche an der Kante 46 der Mantelwandung 38 radial nach außen abragen und an der Innenfläche 48 der Reibringhälfte 22 anliegen. Alternativ können die Laschen 42 auch nicht in Aufnahmeöffnungen der Reibringhälfte 22 eingreifen, sondern vielmehr an der Reibfläche 18 der zweiten Reibringhälfte 22 anliegen. Durch die jeweiligen Abstände zwischen Laschen 42 und Halteelementen 44 kann eine schwimmende Lagerung des Reibringes 14 am Bremsscheibentopf 12 erzielt werden, so dass ein gewisses Spiel in axialer Richtung bestehen bleibt. Damit können beispielsweise unterschiedliche Wärmeausdehnungen des Reibrings 14 und des Bremsscheibentopfes 12 ausgeglichen werden.A designated as a whole with 10 brake disc comprises a brake disc hub 12 and a friction ring 14. The friction ring has two friction surfaces 16, 18 which come in operation of the brake in tribological contact with the brake shoes. Due to the particularly good frictional properties such friction rings 14 are usually made of cast iron, in particular gray cast iron. In order to dissipate the heat occurring during braking operation, the friction ring 14 is designed as an internally ventilated friction ring and consists of two friction ring halves 20, 22 which are interconnected via connecting knobs 24, which are not all designated for clarity. As a result, 26 channels 26 are formed between the friction ring halves 20, through which ambient air can flow and thus dissipate heat. Also in the friction ring halves 20, 22 each channels 28 are introduced, which open into the channels 26 and on the friction surfaces 16, 18 exit to further improve the air flow of the friction ring 14. The brake disk cup 12 has an end face 30, into which openings 32, 34 are inserted, so as to connect the brake disk cup with a hub. Furthermore, the brake disk cup 12 has a jacket wall 38, via which the brake disk cup 12 is connected to the friction ring 14. Since no requirements are made with respect to its friction properties to the brake disk hub 12, this can be carried out to save weight instead of cast iron from sheet metal, such as steel. In order to secure brake disk cup 12 and friction ring 14 against each other, the casing wall 38 of the brake disk cup 12 has a tooth profile which engages in a complementary profile of an inner casing wall 40 of the friction ring 12. As a result, a radial securing of the friction ring 14 with respect to the brake disk hub 12 is achieved, so that torques between the two parts 12, 14 can be transmitted. In order to produce an axial securing between the brake disk cup 12 and the friction ring 14, tabs 42 are punched out of the casing wall 38, which engage in complementary openings of the friction ring 14, which can not be seen in the drawing. A further axial securing is produced by holding elements 44, which project radially outward at the edge 46 of the jacket wall 38 and bear against the inner surface 48 of the friction ring half 22. Alternatively, the tabs 42 can not engage in receiving openings of the friction ring half 22, but rather abut against the friction surface 18 of the second friction ring half 22. Due to the respective distances between tabs 42 and retaining elements 44, a floating mounting of the friction ring 14 on the brake disk hub 12 can be achieved, so that a certain amount of play remains in the axial direction. Thus, for example, different thermal expansions of the friction ring 14 and the brake disk hub 12 can be compensated.
Wie Fig. 3 zu entnehmen ist, ist die Verzahnung zwischen Reibring 14 und Bremsscheibentopf 12 asymmetrisch ausgebildet, wobei die Zähne 50 des Bremsscheibentopfes 12 schmaler ausgeführt sind als die Zähne 52 des Reibringes 14. Die Lückenweite d1 der Verzahnung des Reibringes 14 beträgt dabei 4,5 bis 6 mm, die Lückenweite d2 der Verzahnung des Bremsscheibentopfes 12 7,5 bis 9,5 mm. Der Flankenwinkel α der Verzahnung des Bremsscheibentopfes liegt zwischen 55° und 65°. Durch eine derartige asymmetrische und engmaschige Verzahnung von Bremsscheibentopf 12 und Reibring 14 wird eine besonders gute und verschleißarme Drehmomentenübertragung zwischen Bremsscheibentopf 12 und Reibring 14 erzielt. Fig. 4A und B zeigen eine alternative Ausführungsform, bei welcher eine Lasche 52 an der Kante der Mantelwandung des Bremsscheibentopfes den Reibring umgreift, wobei eine Gegensicherung durch einen Anschlag 54 bereitgestellt wird. 3, the toothing between the friction ring 14 and the brake disk hub 12 is formed asymmetrically, wherein the teeth 50 of the brake disk hub 12 are made narrower than the teeth 52 of the friction ring 14. The gap width d1 of the toothing of the friction ring 14 is 4, 5 to 6 mm, the gap width d2 of the teeth of the brake disk hub 12 7.5 to 9.5 mm. The flank angle α of the teeth of the brake disk hub is between 55 ° and 65 °. Such an asymmetrical and closely meshed toothing of the brake disk cup 12 and the friction ring 14 achieves a particularly good and low-wear torque transmission between the brake disk cup 12 and the friction ring 14. 4A and B show an alternative embodiment in which a tab 52 engages around the edge of the jacket wall of the brake disk hub, the friction ring, wherein a counter-lock is provided by a stop 54.

Claims

Patentansprüche claims
1. Bremsscheibe (10) für einen Kraftwagen, mit einem Bremsscheibentopf (12) und einem zu diesem koaxial angeordneten Reibring (14), wobei eine äußere Mantelfläche (38) des Bremsscheibentopfes ein Profil aufweist, welches zur Drehmomentübertragung in ein komplementäres Profil einer inneren Mantelfläche (40) des Reibringes (14) eingreift, und wobei der Reibring (14) axial gesichert an dem Bremsscheibentopf (12) angeordnet ist, dadurch gekennzeichnet, dass an der äußeren Mantelfläche (38) des Bremsscheibentopfes (12) wenigstens eine1. brake disc (10) for a motor vehicle, with a brake disc hub (12) and a coaxially arranged for this friction ring (14), wherein an outer circumferential surface (38) of the brake disc hub has a profile which for torque transmission in a complementary profile of an inner circumferential surface (40) of the friction ring (14) engages, and wherein the friction ring (14) axially secured to the brake disk chamber (12) is arranged, characterized in that on the outer circumferential surface (38) of the brake disk hub (12) at least one
Lasche (42) zur axialen Ausrichtung ausgebildet ist.Tab (42) is formed for axial alignment.
2. Bremsscheibe (10) nach Anspruch 1 , dadurch gekennzeichnet, dass die Lasche (42) zur axialen Sicherung aus der Wandung (38) des Bremsscheibentopfes (12) ausgestanzt und umgebogen ist.2. Brake disc (10) according to claim 1, characterized in that the tab (42) for axial securing from the wall (38) of the brake disc hub (12) is punched out and bent.
3. Bremsscheibe (10) nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass wenigstens eine Durchsetzung (54) in der Wandung (38) des Bremsscheibentopfes (12) zur axialen Ausrichtung vorgesehen ist.3. Brake disc (10) according to claim 1 or 2, characterized in that at least one enforcement (54) in the wall (38) of the brake disc hub (12) is provided for axial alignment.
4. Bremsscheibe (10) nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Lasche (42) in eine Öffnung des Reibringes (14) eingreift oder an einer Fläche (18) des Reibringes (14) anliegt. 4. Brake disc (10) according to claim 1 or 2, characterized in that the tab (42) engages in an opening of the friction ring (14) or on a surface (18) of the friction ring (14).
5. Bremsscheibe (10) nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass an einer Kante (40) der äußeren Mantelfläche (38) des Bremsscheibentopfes (12) wenigstens ein radial abragendes Halteelement (44, 52) ausgebildet ist, welches wenigstens teilweise an einer Stirnfläche (46) des Reibrings (14) anliegt.5. Brake disc (10) according to one of claims 1 to 4, characterized in that at one edge (40) of the outer circumferential surface (38) of the brake disc hub (12) at least one radially projecting retaining element (44, 52) is formed, which at least partially abuts an end face (46) of the friction ring (14).
6. Bremsscheibe (10) nach Anspruch 5, dadurch gekennzeichnet, dass das Halteelement (44, 52) und/oder die Lasche (44) durch Umformung erzeugten elastisch-plastischen Charakter aufweist.6. Brake disc (10) according to claim 5, characterized in that the holding element (44, 52) and / or the tab (44) produced by deformation elastic-plastic character.
7. Bremsscheibe (10) nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die Profile von Reibring (12) und Bremsscheibentopf (14) als Verzahnung ausgebildet sind.7. Brake disc (10) according to one of claims 1 to 4, characterized in that the profiles of the friction ring (12) and brake disc hub (14) are formed as a toothing.
8. Bremsscheibe (10) nach Anspruch 5, dadurch gekennzeichnet, dass ein Flankenwinkel (α) der Verzahnung des Bremsscheibentopfes (12) 55° bis 65° beträgt.8. Brake disc (10) according to claim 5, characterized in that a flank angle (α) of the toothing of the brake disc hub (12) is 55 ° to 65 °.
9. Bremsscheibe (10) nach Anspruch 5 oder 6, dadurch gekennzeichnet, dass die Verzahnung zwischen Reibring (12) und Bremsscheibentopf (14) asymmetrisch ausgebildet ist.9. Brake disc (10) according to claim 5 or 6, characterized in that the toothing between the friction ring (12) and the brake disc hub (14) is formed asymmetrically.
10. Bremsscheibe (10) nach Anspruch 7, dadurch gekennzeichnet, dass eine Lückenweite (d1 ) der Verzahnung des Reibrings (14) 4,5 bis 6 mm beträgt.10. Brake disc (10) according to claim 7, characterized in that a gap width (d1) of the toothing of the friction ring (14) is 4.5 to 6 mm.
11. Bremsscheibe (10) nach Anspruch 7 oder 8, dadurch gekennzeichnet, dass eine Lückenweite (d2) der Verzahnung des Bremsscheibentopfes (12) 7,5 bis 9,5 mm beträgt. 11. Brake disc (10) according to claim 7 or 8, characterized in that a gap width (d2) of the toothing of the brake disc hub (12) is 7.5 to 9.5 mm.
12. Bremsscheibe (10) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Bremsscheibentopf (12) aus Stahl ausgebildet ist.12. Brake disc (10) according to any one of the preceding claims, characterized in that the brake disc hub (12) is formed of steel.
13. Kraftwagen mit einer Bremsscheibe (10) nach einem der vorhergehenden Ansprüche. 13. Motor vehicle with a brake disc (10) according to one of the preceding claims.
EP10706920A 2009-03-07 2010-02-11 Brake disk Withdrawn EP2404075A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009012216A DE102009012216A1 (en) 2009-03-07 2009-03-07 brake disc
PCT/EP2010/000863 WO2010102704A1 (en) 2009-03-07 2010-02-11 Brake disk

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EP2404075A1 true EP2404075A1 (en) 2012-01-11

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US (1) US20120085603A1 (en)
EP (1) EP2404075A1 (en)
JP (1) JP2012519806A (en)
CN (1) CN102341612A (en)
DE (1) DE102009012216A1 (en)
WO (1) WO2010102704A1 (en)

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WO2010102704A1 (en) 2010-09-16
DE102009012216A1 (en) 2010-09-09
CN102341612A (en) 2012-02-01
JP2012519806A (en) 2012-08-30

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