WO1995014869A1 - Brake plunger for disk brakes - Google Patents

Brake plunger for disk brakes Download PDF

Info

Publication number
WO1995014869A1
WO1995014869A1 PCT/EP1994/003827 EP9403827W WO9514869A1 WO 1995014869 A1 WO1995014869 A1 WO 1995014869A1 EP 9403827 W EP9403827 W EP 9403827W WO 9514869 A1 WO9514869 A1 WO 9514869A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
annular groove
piston
brake piston
groove
Prior art date
Application number
PCT/EP1994/003827
Other languages
German (de)
French (fr)
Inventor
Rudolf Thiel
Andreas Döll
Original Assignee
Itt Automotive Europe 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 Itt Automotive Europe Gmbh filed Critical Itt Automotive Europe Gmbh
Priority to EP95900762A priority Critical patent/EP0729552A1/en
Publication of WO1995014869A1 publication Critical patent/WO1995014869A1/en

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
    • F16D65/0973—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces
    • F16D65/0979—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces acting on the rear side of the pad or an element affixed thereto, e.g. spring clips securing the pad to the brake piston or caliper
    • 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
    • F16D2125/00—Components of actuators
    • F16D2125/02—Fluid-pressure mechanisms
    • F16D2125/06—Pistons

Definitions

  • the invention relates to a brake piston for disc brakes according to the preamble of patent claim 1.
  • the known brake piston has an annular groove which is introduced into its outer lateral surface and is used to fasten a protective cap.
  • An annular groove made in the inner wall surface of the hollow brake piston is provided for the engagement of a retaining spring of a brake pad.
  • the outer and the inner ring groove are arranged approximately at the same height in the axial direction, so that the wall thickness of the brake piston is greatly reduced in the area of the ring grooves.
  • the overall wall thickness of the brake piston is dimensioned relatively large. As a result, the known brake piston has a relatively high weight.
  • the object of the invention is to provide a brake piston for disc brakes which has an advantageously low weight without the minimum wall thickness falling below a value required for the transmission of the application force from the brake piston to the brake lining.
  • the solution to the problem results from the characterizing part of patent claim 1.
  • the solution is to arrange the two annular grooves so far from each other in the axial direction that the narrowing of the Wall thickness in the area of the inner ring groove cannot add to the constriction in the area of the outer ring groove.
  • the overall wall thickness can be made smaller without falling below a minimum wall thickness in the area of the ring grooves. This results in an advantageously low weight of the brake piston according to the invention.
  • the inner annular groove is arranged closer to the piston head in the axial direction than the outer annular groove.
  • the outer annular groove is therefore closer to the end section of the brake piston protruding from the cylinder bore of the disc brake. In the reverse case, this end section would have to protrude much further out of the cylinder bore, as a result of which the need for axial installation space is increased.
  • the total wall thickness between the outer lateral surface and the inner wall surface of the brake piston is approximately equal to the sum of the depth of the inner annular groove and the depth of the outer annular groove, a relatively light brake piston is obtained in which the maximum possible clamping force is relatively large. It is advantageous to provide approximately the same depth for the inner and the outer annular groove. The remaining wall thickness then remains approximately half the total wall thickness. In this case, the smallest distance between a wall of the inner annular groove and a wall of the outer annular groove is best designed to be the same or, in order to avoid a larger displacement of the annular grooves to one another, slightly larger than the reduced wall thickness or half the total wall thickness of the brake piston.
  • the inner annular groove has a groove flank closest to the open end of the brake piston, which is arranged perpendicular to the piston axis.
  • This groove flank forms with the inner wall surface of the brake piston a circumferential edge against which a retaining spring of a brake pad rests and can generate an axial force component that holds the brake pad in contact with the brake piston.
  • Claims 7 to 10 are also intended to protect a disc brake equipped with a brake piston according to the invention.
  • the retaining spring of a brake piston provided for engagement in the inner annular groove is provided with extended spring tongues in order to reach the inner annular groove which is offset towards the piston crown.
  • the spring characteristic becomes softer due to the lengthening of the spring tongues, so that the spring tongues must be stiffened according to the features of claim 7 to compensate for them by additional deformations in order to ensure a firm hold of the retaining spring in the brake piston.
  • Such shaping can take place according to claim 8 by bending an edge of the retaining spring running between two opposite spring tongues.
  • the indentations can also consist of embossed beads which are embossed in the area of the retaining spring located between two opposing spring tongues.
  • Claim 11 relates to a retaining spring per se, which is designed in a particularly advantageous manner in connection with a brake lining for a disc brake according to one of Claims 7 to 9.
  • Claim 12 relates to a brake lining per se provided with a retaining spring according to claim 11.
  • FIG. 1 shows a brake piston according to the invention in section with a protective cap which engages in the outer annular groove and a retaining spring of a partially illustrated brake pad which engages in the inner annular groove;
  • Figure 2 is an enlarged partial view of the brake piston of Figure 1;
  • Figure 3 is a partial view like Figure 2, but of another brake piston
  • Figure 4 is a plan view of a retaining spring in a first embodiment
  • Figure 5 is a side view from direction B of Figure 4.
  • Figure 6 is a perspective view of the same retaining spring
  • FIG. 7 is a plan view of a retaining spring in a second embodiment
  • FIG. 8 shows an enlarged section along line AA of FIG. 7.
  • the hollow cylindrical section 3 has an inner wall surface 4 and an outer circumferential surface 5.
  • An inner annular groove 6 is introduced into the inner wall surface 4 and an outer annular groove 7 is introduced into the outer circumferential surface 5.
  • a brake lining 9 rests with its back plate 10 on an end face 8 of the brake piston 1.
  • a retaining spring 11 is riveted from spring plate.
  • the retaining spring 11 has two spring tongues 12, 13 which start from a central section 14 of the retaining spring 11 and protrude obliquely from the latter.
  • the two spring tongues 12, 13 are intended for fastening the retaining spring 11 and thus the brake pad 9 to the brake piston 1.
  • the spring tongues 12, 13 arranged opposite one another engage in the inner annular groove 6 of the brake piston 1.
  • a third spring tongue 15 extends essentially perpendicularly to the other two spring tongues 12, 13 also from the central section 14, initially runs in the direction of the piston crown 2, and then after a bend of almost 180 ° away from the piston crown 2 and obliquely to the inner one Wall surface 4 to run.
  • the tongue end 16 of the third spring tongue 15 lies very close to the open end of the brake piston 1 on the inner wall surface 4.
  • the third spring tongue 15 serves to hold the brake pad 9 down against its guide surfaces (not shown) in order to prevent the brake pad 9 from rattling.
  • An annular bead 17 of a protective cap 18 engages in the outer annular groove 5, the other end of the protective cap 18 is fastened to the disc brake housing (not shown) and serves to protect the outer lateral surface 5 from dirt.
  • the inner annular groove 6 is arranged offset in the axial direction 19 with respect to the outer annular groove 7, to the extent that the reduced wall thickness 20 of the brake piston 1 due to the outer annular groove 7 is caused by the insertion the inner annular groove 6 is not further reduced.
  • the two annular grooves 6, 7 are of approximately the same depth with respect to the inner wall surface 4 and the outer jacket surface 5, the sum of the two depths corresponding approximately to the total wall thickness 21 of the brake piston 1.
  • the inner annular groove 6 is axially offset relative to the outer annular groove 7 in the direction of the piston crown 2 so that the smallest distance 22 between a wall of the inner annular groove 6 and a wall of the outer annular groove 7 is the same as that caused by the introduction of the outer annular groove 7 reduced wall thickness is 20. If the inner annular groove 6 is displaced axially further in the direction of the piston crown 2, the smallest distance 22 becomes greater than the reduced wall thickness 20. This measure would, however, require a further extension of the spring tongues 12, 13.
  • a section of a modified brake piston 1 ' is shown in FIG. 3, in which a modified inner annular groove 6' is arranged in the axial region of the outer annular groove 7.
  • the modified brake piston 1 ' requires a much larger overall wall thickness 21', so do not reduce the reduced wall thickness 20 even further.
  • Self-confidence Of course, the modified brake piston 1 'is much heavier than the brake piston 1 according to the invention, given the same performance with regard to the transmission of the application force to the brake lining 9.
  • the retaining spring 11 is inserted into the cavity of the brake piston 1.
  • the spring tongues 12, 13, 15 are biased in the radial direction towards the piston axis. Shortly before the back plate 10 comes into contact with the end face 8, the two spring tongues 12, 13 engage in the inner annular groove 6.
  • the inner annular groove 6 has a trapezoidal cross section with a groove bottom 23 arranged parallel to the piston axis and two groove flanks 24, 25.
  • the groove flank 25 closest to the open end of the brake piston 1 is perpendicular to the piston axis and the other groove flank 24 is arranged obliquely thereto.
  • the inner annular groove 6 is arranged axially displaced in the direction of the piston crown 2, the two spring tongues 12, 13 must be made relatively long in order to be able to engage in the inner annular groove 6.
  • the spring characteristic becomes "softer” and the holding force or the axial force component mentioned is too low. Additional indentations are therefore provided to stiffen the retaining spring 11.
  • the lower edge 27 of the central section 14, on which there is no spring tongue, is stiffened by bending through 90 °.
  • FIGS. 7 and 8 Another embodiment of the invention is shown in FIGS. 7 and 8. Here you can see a modified retaining spring 11 ', whose modified central section 14' is provided with embossed beads 28, 29 for reinforcement.
  • the modified retaining spring 11 'does not differ from the retaining spring 11 described above.
  • the back plate 10 is provided with an embossed projection on which the retaining spring 11 is placed, so that the projection protrudes through the opening 30. The projection is then tumbled and riveted to the retaining spring 11 on the brake pad 9.

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

Abstract

A beaker-shaped brake plunger (1) for disk brakes is provided with an inner ring groove (6) for engaging a retaining spring (11) for securing a brake lining (9), and an outer ring groove (7) for securing a protective cover (18). According to the invention, the inner ring groove (6) is longitudinally displaced relative to the outer ring groove (7) sufficiently to ensure that the wall thickness (20) of the brake plunger (1), which is reduced by the outer ring groove (7), is not further reduced by the other ring groove (6). The reduced wall thickness (20) is sufficient to transmit the brake application force to the brake lining (9), while the full wall thickness (21) of the brake plunger (1) is advantageously low. The brake plunger (1) thus has the advantage of reduced weight, without any loss of efficiency.

Description

Bremskolben für ScheibenbremsenBrake pistons for disc brakes
Die Erfindung betrifft einen Bremskolben für Scheibenbrem¬ sen gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a brake piston for disc brakes according to the preamble of patent claim 1.
Aus der DE 39 21 346 AI ist eine Scheibenbremse mit einem gattungsgemäßen Bremskolben bekannt. Der bekannte Bremskol¬ ben besitzt eine Ringnut, die in seine äußere Mantelfläche eingebracht ist und zur Befestigung einer Schutzkappe dient. Eine in die innere Wandfläche des hohlen Bremskol¬ bens eingebrachte Ringnut ist für den Eingriff einer Halte¬ feder eines Bremsbelags vorgesehen. Die äußere und die in¬ nere Ringnut sind in axialer Richtung ungefähr auf dersel¬ ben Höhe angeordnet, so daß die Wandstärke des Bremskolbens im Bereich der Ringnuten stark vermindert wird. Um zwischen den beiden Ringnuten eine genügende Restwandstärke aufrecht zu erhalten, ist die Gesamtwandstärke des Bremskolbens re¬ lativ groß dimensioniert. Dadurch hat der bekannte Brems¬ kolben ein relativ hohes Gewicht.From DE 39 21 346 AI a disc brake with a generic brake piston is known. The known brake piston has an annular groove which is introduced into its outer lateral surface and is used to fasten a protective cap. An annular groove made in the inner wall surface of the hollow brake piston is provided for the engagement of a retaining spring of a brake pad. The outer and the inner ring groove are arranged approximately at the same height in the axial direction, so that the wall thickness of the brake piston is greatly reduced in the area of the ring grooves. In order to maintain a sufficient residual wall thickness between the two ring grooves, the overall wall thickness of the brake piston is dimensioned relatively large. As a result, the known brake piston has a relatively high weight.
Aufgabe der Erfindung ist es, einen Bremskolben für Schei¬ benbremsen anzugeben, der ein vorteilhaft geringes Gewicht aufweist, ohne daß die minimale Wandstärke einen für die Übertragung der Zuspannkraft vom Bremskolben auf den Brems¬ belag erforderlichen Wert unterschreitet.The object of the invention is to provide a brake piston for disc brakes which has an advantageously low weight without the minimum wall thickness falling below a value required for the transmission of the application force from the brake piston to the brake lining.
Die Lösung der Aufgabe ergibt sich aus dem kennzeichnenden Teil des Patentanspruchs 1. Im Prinzip besteht die Lösung darin, die beiden Ringnuten in axialer Richtung soweit ge¬ geneinander versetzt anzuordnen, daß sich die Verengung der Wandstärke im Bereich der inneren Ringnut nicht zur Veren¬ gung im Bereich der äußeren Ringnut addieren kann. Bei dem erfindungsgemäßen Bremskolben kann die Gesamtwandstärke ge¬ ringer ausgebildet werden, ohne daß im Bereich der Ringnu¬ ten eine minimale Wandstärke unterschritten wird. Daraus resultiert ein vorteilhaft geringes Gewicht des erfindungs¬ gemäßen Bremskolbens.The solution to the problem results from the characterizing part of patent claim 1. In principle, the solution is to arrange the two annular grooves so far from each other in the axial direction that the narrowing of the Wall thickness in the area of the inner ring groove cannot add to the constriction in the area of the outer ring groove. In the brake piston according to the invention, the overall wall thickness can be made smaller without falling below a minimum wall thickness in the area of the ring grooves. This results in an advantageously low weight of the brake piston according to the invention.
In einer bevorzugten Ausführungsform gemäß Anspruch 2 ist die innere Ringnut in axialer Richtung näher am Kolbenboden angeordnet als die äußere Ringnut. Die äußere Ringnut liegt also näher an dem aus der Zylinderbohrung der Scheibenbrem¬ se herausragenden Endabschnitt des Bremskolbens. Im umge¬ kehrten Falle müßte dieser Endabschnitt sehr viel weiter aus der Zylinderbohrung herausragen, wodurch sich der Be¬ darf an axialem Einbauraum vergrößert.In a preferred embodiment according to claim 2, the inner annular groove is arranged closer to the piston head in the axial direction than the outer annular groove. The outer annular groove is therefore closer to the end section of the brake piston protruding from the cylinder bore of the disc brake. In the reverse case, this end section would have to protrude much further out of the cylinder bore, as a result of which the need for axial installation space is increased.
Wenn die gesamte Wandstärke zwischen der äußeren Mantel¬ fläche und der inneren Wandfläche des Bremskolbens gemäß Anspruch 3 ungefähr gleich der Summe aus der Tiefe der in¬ neren Ringnut und der Tiefe der äußeren Ringnut ist, erhält man einen relativ leichten Bremskolben, bei dem die maximal mögliche Zuspannkraft relativ groß ist. Dabei ist es vor¬ teilhaft, gemäß Anspruch 4 für die innere und die äußere Ringnut ungefähr die gleiche Tiefe vorzusehen. Als Rest¬ wandstärke bleibt dann ungefähr die halbe Gesamtwandstärke. In diesem Fall wird gemäß Anspruch 5 der kleinste Abstand zwischen einer Wand der inneren Ringnut und einer Wand der äußeren Ringnut am besten gleich oder zur Vermeidung einer größeren Versetzung der Ringnuten zueinander geringfügig größer als die verminderte Wandstärke oder die halbe Ge¬ samtwandstärke des Bremskolbens ausgelegt. In einer Weiterbildung der Erfindung gemäß Anspruch 6 weist die innere Ringnut eine dem offenen Ende des Bremskolbens nächstliegende Nutflanke auf, die senkrecht zur Kolbenachse angeordnet ist. Diese Nutflanke bildet mit der inneren Wandfläche des Bremskolbens eine umlaufende Kante, an der eine Haltefeder eines Bremsbelags anliegen und eine axiale Kraftkomponente erzeugen kann, die den Bremsbelag in Anlage am Bremskolben hält.If the total wall thickness between the outer lateral surface and the inner wall surface of the brake piston is approximately equal to the sum of the depth of the inner annular groove and the depth of the outer annular groove, a relatively light brake piston is obtained in which the maximum possible clamping force is relatively large. It is advantageous to provide approximately the same depth for the inner and the outer annular groove. The remaining wall thickness then remains approximately half the total wall thickness. In this case, the smallest distance between a wall of the inner annular groove and a wall of the outer annular groove is best designed to be the same or, in order to avoid a larger displacement of the annular grooves to one another, slightly larger than the reduced wall thickness or half the total wall thickness of the brake piston. In a development of the invention according to claim 6, the inner annular groove has a groove flank closest to the open end of the brake piston, which is arranged perpendicular to the piston axis. This groove flank forms with the inner wall surface of the brake piston a circumferential edge against which a retaining spring of a brake pad rests and can generate an axial force component that holds the brake pad in contact with the brake piston.
Mit den Ansprüchen 7 bis 10 soll auch eine mit einem erfin¬ dungsgemäßen Bremskolben ausgestattete Scheibenbremse ge¬ schützt werden. Gemäß Anspruch 7 ist die zum Eingriff in die innere Ringnut vorgesehene Haltefeder eines Bremskol¬ bens mit verlängerten Federzungen versehen, um die zum Kol¬ benboden hin versetzt angeordnete innere Ringnut zu er¬ reichen. Durch die Verlängerung der Federzungen wird die FederCharakteristik weicher, so daß die Federzungen gemäß den Merkmalen des Anspruchs 7 zum Ausgleich durch zusätz¬ liche Einformungen versteift werden müssen, um einen festen Halt der Haltefeder im Bremskolben zu gewährleisten. Eine derartige Einformung kann gemäß Anspruch 8 durch Umbiegen eines zwischen zwei gegenüberliegenden Federzungen verlau¬ fenden Randes der Haltefeder erfolgen. Die Einformungen können aber auch gemäß Anspruch 9 aus eingeprägten Sicken bestehen, die in dem zwischen zwei gegenüberliegenden Fe¬ derzungen befindlichen Bereich der Haltefeder eingeprägt sind.Claims 7 to 10 are also intended to protect a disc brake equipped with a brake piston according to the invention. According to claim 7, the retaining spring of a brake piston provided for engagement in the inner annular groove is provided with extended spring tongues in order to reach the inner annular groove which is offset towards the piston crown. The spring characteristic becomes softer due to the lengthening of the spring tongues, so that the spring tongues must be stiffened according to the features of claim 7 to compensate for them by additional deformations in order to ensure a firm hold of the retaining spring in the brake piston. Such shaping can take place according to claim 8 by bending an edge of the retaining spring running between two opposite spring tongues. However, the indentations can also consist of embossed beads which are embossed in the area of the retaining spring located between two opposing spring tongues.
Insbesondere in Verbindung mit einem Bremskolben nach An¬ spruch 6 ist eine Ausführungsform der Scheibenbremse gemäß Anspruch 10 vorgesehen, bei der durch Anlage der genannten Federzungen an einer Kante der inneren Ringnut eine axiale Kraftkomponente zum Andruck des Bremsbelags an den Brems¬ kolben erzeugt wird. Anspruch 11 bezieht sich auf eine Haltefeder an sich, die in Verbindung mit einem Bremsbelag für eine Scheibenbremse gemäß einem der Ansprüche 7 bis 9 in besonders vorteilhaf¬ ter Weise ausgebildet ist. Anspruch 12 bezieht sich auf ei¬ nen mit einer Haltefeder nach Anspruch 11 versehenen Brems¬ belag an sich.In particular in connection with a brake piston according to claim 6, an embodiment of the disc brake is provided according to claim 10, in which an axial force component for pressing the brake lining against the brake piston is generated by the abovementioned spring tongues on one edge of the inner annular groove. Claim 11 relates to a retaining spring per se, which is designed in a particularly advantageous manner in connection with a brake lining for a disc brake according to one of Claims 7 to 9. Claim 12 relates to a brake lining per se provided with a retaining spring according to claim 11.
Ausführungsbeispiele der Erfindung werden nachfolgend an¬ hand der Zeichnungen näher erläutert.Exemplary embodiments of the invention are explained in more detail below with reference to the drawings.
Es zeigen:Show it:
Figur 1 einen erfindungsgemäßen Bremskolben im Schnitt mit in die äußere Ringnut eingreifender Schutzkappe und in die innere Ringnut eingreifender Haltefeder eines teilweise dargestellten Bremsbelags;1 shows a brake piston according to the invention in section with a protective cap which engages in the outer annular groove and a retaining spring of a partially illustrated brake pad which engages in the inner annular groove;
Figur 2 eine vergrößerte Teilansicht des Bremskolbens von Figur 1;Figure 2 is an enlarged partial view of the brake piston of Figure 1;
Figur 3 eine Teilansicht wie Figur 2, aber eines anderen Bremskolbens;Figure 3 is a partial view like Figure 2, but of another brake piston;
Figur 4 eine Draufsicht auf eine Haltefeder in einer er¬ sten Ausführungsform;Figure 4 is a plan view of a retaining spring in a first embodiment;
Figur 5 eine Seitenansicht aus Richtung B von Figur 4;Figure 5 is a side view from direction B of Figure 4;
Figur 6 eine perspektivische Ansicht derselben Haltefeder;Figure 6 is a perspective view of the same retaining spring;
Figur 7 eine Draufsicht auf eine Haltefeder in einer zwei¬ ten Ausführungsform; Figur 8 einen vergrößerten Schnitt gemäß Linie A-A von Fi¬ gur 7.Figure 7 is a plan view of a retaining spring in a second embodiment; FIG. 8 shows an enlarged section along line AA of FIG. 7.
In Figur 1 erkennt man einen becherförmigen Bremskolben 1 mit einem Kolbenboden 2, der in einen hohlzylindrischen Ab¬ schnitt 3 übergeht. Der hohlzylindrische Abschnitt 3 be¬ sitzt eine innere Wandfläche 4 und eine äußere Mantelfläche 5. In die innere Wandfläche 4 ist eine innere Ringnut 6 und in die äußere Mantelfläche 5 eine äußere Ringnut 7 einge¬ bracht.1 shows a cup-shaped brake piston 1 with a piston head 2 which merges into a hollow cylindrical section 3. The hollow cylindrical section 3 has an inner wall surface 4 and an outer circumferential surface 5. An inner annular groove 6 is introduced into the inner wall surface 4 and an outer annular groove 7 is introduced into the outer circumferential surface 5.
An einer Stirnfläche 8 des Bremskolbens 1 liegt ein Brems¬ belag 9 mit seiner Rückenplatte 10 an. Auf der Rückenplatte 10 ist eine Haltefeder 11 aus Federblech angenietet. Die Haltefeder 11 besitzt zwei Federzungen 12, 13, die von ei¬ nem Mittelabschnitt 14 der Haltefeder 11 ausgehen und von diesem schräg abstehen. Die beiden Federzungen 12, 13 sind zur Befestigung der Haltefeder 11 und damit des Bremsbelags 9 am Bremskolben 1 bestimmt. Für diesen Zweck greifen die gegenüberliegend angeordneten Federzungen 12, 13 in die in¬ nere Ringnut 6 des Bremskolbens 1 ein. Eine dritte Feder¬ zunge 15 geht im wesentlichen senkrecht zu den anderen bei¬ den Federzungen 12, 13 ebenfalls vom Mittelabschnitt 14 aus, verläuft zunächst in Richtung Kolbenboden 2, um dann nach einer Biegung von nahezu 180° vom Kolbenboden 2 weg und schräg zur inneren Wandfläche 4 hin zu verlaufen. Das Zungenende 16 der dritten Federzunge 15 liegt ganz in der Nähe des offenen Endes des Bremskolbens 1 an der inneren Wandfläche 4 an. Die dritte Federzunge 15 dient zum Nieder¬ halten des Bremsbelags 9 gegen seine nicht gezeigten Füh¬ rungsflächen, um ein Klappern des Bremsbelags 9 zu verhin¬ dern. In die äußere Ringnut 5 greift ein Ringwulst 17 einer Schutzkappe 18 ein, die Schutzkappe 18 ist mit ihrem ande¬ ren, nicht gezeigten Ende am nicht gezeigten Gehäuse der Scheibenbremse befestigt und dient dazu, die äußere Mantel¬ fläche 5 vor Schmutz zu schützen.A brake lining 9 rests with its back plate 10 on an end face 8 of the brake piston 1. On the back plate 10, a retaining spring 11 is riveted from spring plate. The retaining spring 11 has two spring tongues 12, 13 which start from a central section 14 of the retaining spring 11 and protrude obliquely from the latter. The two spring tongues 12, 13 are intended for fastening the retaining spring 11 and thus the brake pad 9 to the brake piston 1. For this purpose, the spring tongues 12, 13 arranged opposite one another engage in the inner annular groove 6 of the brake piston 1. A third spring tongue 15 extends essentially perpendicularly to the other two spring tongues 12, 13 also from the central section 14, initially runs in the direction of the piston crown 2, and then after a bend of almost 180 ° away from the piston crown 2 and obliquely to the inner one Wall surface 4 to run. The tongue end 16 of the third spring tongue 15 lies very close to the open end of the brake piston 1 on the inner wall surface 4. The third spring tongue 15 serves to hold the brake pad 9 down against its guide surfaces (not shown) in order to prevent the brake pad 9 from rattling. An annular bead 17 of a protective cap 18 engages in the outer annular groove 5, the other end of the protective cap 18 is fastened to the disc brake housing (not shown) and serves to protect the outer lateral surface 5 from dirt.
Wie man am besten in Figur 2 erkennt, ist die innere Ring¬ nut 6 gegenüber der äußeren Ringnut 7 in axialer Richtung 19 versetzt angeordnet, und zwar soviel, daß die aufgrund der äußeren Ringnut 7 verringerte Wandstärke 20 des Brems- kolbens 1 durch das Einbringen der inneren Ringnut 6 nicht noch weiter vermindert wird. Die beiden Ringnuten 6, 7 sind gegenüber der inneren Wandfläche 4 bzw. der äußeren Mantel¬ fläche 5 etwa gleich tief ausgebildet, wobei die Summe der beiden Tiefen ungefähr der Gesamtwandstärke 21 des Brems¬ kolbens 1 entspricht. Dabei ist die innere Ringnut 6 gegen¬ über der äußeren Ringut 7 soweit in Richtung Kolbenboden 2 axial versetzt, daß der kleinste Abstand 22 zwischen einer Wand der inneren Ringnut 6 und einer Wand der äußeren Ring¬ nut 7 gleich der durch das Einbringen der äußeren Ringnut 7 verminderten Wandstärke 20 ist. Wenn man die innere Ringnut 6 noch weiter in Richtung Kolbenboden 2 axial versetzt, wird der kleinste Abstand 22 größer als die verminderte Wandstärke 20. Diese Maßnahme würde aber eine weitere Ver¬ längerung der Federzungen 12, 13 erfordern.As can best be seen in FIG. 2, the inner annular groove 6 is arranged offset in the axial direction 19 with respect to the outer annular groove 7, to the extent that the reduced wall thickness 20 of the brake piston 1 due to the outer annular groove 7 is caused by the insertion the inner annular groove 6 is not further reduced. The two annular grooves 6, 7 are of approximately the same depth with respect to the inner wall surface 4 and the outer jacket surface 5, the sum of the two depths corresponding approximately to the total wall thickness 21 of the brake piston 1. The inner annular groove 6 is axially offset relative to the outer annular groove 7 in the direction of the piston crown 2 so that the smallest distance 22 between a wall of the inner annular groove 6 and a wall of the outer annular groove 7 is the same as that caused by the introduction of the outer annular groove 7 reduced wall thickness is 20. If the inner annular groove 6 is displaced axially further in the direction of the piston crown 2, the smallest distance 22 becomes greater than the reduced wall thickness 20. This measure would, however, require a further extension of the spring tongues 12, 13.
Zum Vergleich ist in Figur 3 ein Ausschnitt eines modifi¬ zierten Bremskolbens 1' dargestellt, bei dem eine modifi¬ zierte innere Ringnut 6' im axialen Bereich der äußeren Ringnut 7 angeordnet ist. Im Vergleich mit Figur 2 erkennt man, daß der modifizierte Bremskolben 1' eine sehr viel größere Gesamtwandstärke 21' benötigt, tun die verminderte Wandstärke 20 nicht noch weiter zu vermindern. Selbstver- ständlich ist der modifizierte Bremskolben 1' bei gleichen Leistungen bezüglich der Übertragung der Zuspannkraft auf den Bremsbelag 9 sehr viel schwerer als der erfindungsge¬ mäße Bremskolben 1.For comparison, a section of a modified brake piston 1 'is shown in FIG. 3, in which a modified inner annular groove 6' is arranged in the axial region of the outer annular groove 7. In comparison with FIG. 2, it can be seen that the modified brake piston 1 'requires a much larger overall wall thickness 21', so do not reduce the reduced wall thickness 20 even further. Self-confidence Of course, the modified brake piston 1 'is much heavier than the brake piston 1 according to the invention, given the same performance with regard to the transmission of the application force to the brake lining 9.
Zur Befestigung des Bremsbelags 9 am Bremskolben 1 wird die Haltefeder 11 in den Hohlraum des Bremskolbens 1 einge¬ steckt. Dabei werden die Federzungen 12, 13, 15 in radialer Richtung auf die Kolbenachse zu vorgespannt. Kurz bevor die Rückenplatte 10 in Anlage an die Stirnfläche 8 kommt, grei¬ fen die beiden Federzungen 12, 13 in die innere Ringnut 6 ein. Die inneren Ringnut 6 besitzt einen trapezförmigen Querschnitt mit einem parallel zur Kolbenachse angeordneten Nutboden 23 und zwei Nutflanken 24, 25. Die dem offenen En¬ de des Bremskolbens 1 nächstliegende Nutflanke 25 ist senk¬ recht zur Kolbenachse und die andere Nutflanke 24 schräg dazu angeordnet. Wenn die Federzungen 12, 13 in die innere Ringnut 6 eingreifen, so liegen sie an einer zwischen der Nutflanke 25 und der inneren Wandfläche 4 gebildeten Kante 26 an. Durch diese schräge Anlage der Federzungen 12, 13 wird eine axiale Kraftkomponente erzeugt, die den Bremsbe¬ lag 9 stets in Anlage an der Stirnfläche 8 des Bremskolbens 1 hält.To attach the brake pad 9 to the brake piston 1, the retaining spring 11 is inserted into the cavity of the brake piston 1. The spring tongues 12, 13, 15 are biased in the radial direction towards the piston axis. Shortly before the back plate 10 comes into contact with the end face 8, the two spring tongues 12, 13 engage in the inner annular groove 6. The inner annular groove 6 has a trapezoidal cross section with a groove bottom 23 arranged parallel to the piston axis and two groove flanks 24, 25. The groove flank 25 closest to the open end of the brake piston 1 is perpendicular to the piston axis and the other groove flank 24 is arranged obliquely thereto. When the spring tongues 12, 13 engage in the inner annular groove 6, they rest on an edge 26 formed between the groove flank 25 and the inner wall surface 4. This oblique contact of the spring tongues 12, 13 produces an axial force component which always holds the brake pad 9 in contact with the end face 8 of the brake piston 1.
Da bei einem erfindungsgemäßen Bremskolben 1 die innere Ringnut 6 axial in Richtung Kolbenboden 2 verschoben ange¬ ordnet ist, müssen die beiden Federzungen 12, 13 relativ lang ausgebildet sein, um in die innere Ringnut 6 eingrei¬ fen zu können. Dabei wird die Federcharakteristik "weicher" und die Haltekraft bzw. die genannte axiale Kraftkomponente fällt zu gering aus. Zur Versteifung der Haltefeder 11 sind daher zusätzliche Einformungen vorgesehen. Wie man am besten in den Figuren 4 bis 6 erkennt, ist der untere Rand 27 des Mittelabschnitts 14, an dem sich keine Federzunge befindet, durch Umbiegen um 90° versteift.Since, in a brake piston 1 according to the invention, the inner annular groove 6 is arranged axially displaced in the direction of the piston crown 2, the two spring tongues 12, 13 must be made relatively long in order to be able to engage in the inner annular groove 6. The spring characteristic becomes "softer" and the holding force or the axial force component mentioned is too low. Additional indentations are therefore provided to stiffen the retaining spring 11. As can best be seen in FIGS. 4 to 6, the lower edge 27 of the central section 14, on which there is no spring tongue, is stiffened by bending through 90 °.
Eine andere Ausführungsform der Erfindung ist in den Figu¬ ren 7 und 8 dargestellt. Hier erkennt man eine modifizierte Haltefeder 11', deren modifizierter Mittelabschnitt 14' zur Versteifung mit eingeprägten Sicken 28, 29 versehen ist.Another embodiment of the invention is shown in FIGS. 7 and 8. Here you can see a modified retaining spring 11 ', whose modified central section 14' is provided with embossed beads 28, 29 for reinforcement.
Ansonsten unterscheidet sich die modifizierte Haltefeder 11' nicht von der weiter oben beschriebenen Haltefeder 11. Dies gilt insbesondere für eine im Mittelabschnitt 14 ein¬ gestanzte Öffnung 30 mit quadratischem Querschnitt, die zum Befestigen der Haltefeder 11 am Bremsbelag 9 dient. Die Rückenplatte 10 ist für diesen Zweck mit einem durchgepräg¬ ten Vorsprung versehen, auf dem die Haltefeder 11 aufge¬ setzt wird, so daß der Vorsprung durch die Öffnung 30 ragt. Anschließend wird der Vorsprung vertaumelt und damit die Haltefeder 11 am Bremsbelag 9 vernietet. Otherwise, the modified retaining spring 11 'does not differ from the retaining spring 11 described above. This applies in particular to an opening 30 with a square cross section punched in the central section 14, which is used to fasten the retaining spring 11 to the brake lining 9. For this purpose, the back plate 10 is provided with an embossed projection on which the retaining spring 11 is placed, so that the projection protrudes through the opening 30. The projection is then tumbled and riveted to the retaining spring 11 on the brake pad 9.

Claims

Patentansprüche claims
1. Bremskolben für Scheibenbremsen, mit einem Kolbenboden (2), der becherförmig in einen hohlzylindrischen Ab¬ schnitt (3) mit einer inneren Wandfläche (4) und einer äußeren Wandfläche (5) übergeht, mit einer in die innere Wandfläche (4) eingebrachten inneren Ringnut (6), die für den Eingriff einer Haltefeder (11) eines Bremsbelags (9) und zur Befestigung des Bremsbelags (9) am Bremskol¬ ben (1) bestimmt ist, und mit einer in die äußere Man¬ telfläche (5) eingebrachten äußeren Ringnut (7), die für die Befestigung einer Schutzkappe (18) bestimmt ist, da¬ durch g e k e n n z e i c h n e t, daß die innere Ring¬ nut (6) gegenüber der äußeren Ringnut (7) um soviel axial versetzt angeordnet ist, so daß die aufgrund der einen Ringnut (7) verminderte Wandstärke des Bremskol¬ bens (1) durch das Einbringen der anderen Ringnut (6) nicht noch weiter vermindert wird.1. Brake piston for disc brakes, with a piston head (2), which mugs into a hollow cylindrical section (3) with an inner wall surface (4) and an outer wall surface (5), with one introduced into the inner wall surface (4) inner annular groove (6), which is intended for the engagement of a retaining spring (11) of a brake pad (9) and for fastening the brake pad (9) to the brake piston (1), and with an into the outer jacket surface (5) introduced outer annular groove (7), which is intended for fastening a protective cap (18), characterized in that the inner annular groove (6) is arranged so axially offset relative to the outer annular groove (7) that the due to the reduced wall thickness of the brake piston (1) due to the one annular groove (7), the introduction of the other annular groove (6) does not reduce it further.
2. Bremskolben nach Anspruch 1, dadurch g e k e n n ¬ z e i c h n e t, daß die innere Ringnut (6) in axialer Richtung (19) näher am Kolbenboden (2) angeordnet ist als die äußere Ringnut (7).2. Brake piston according to claim 1, characterized in that the inner annular groove (6) is arranged in the axial direction (19) closer to the piston crown (2) than the outer annular groove (7).
3. Bremskolben nach Anspruch 2, dadurch g e k e n n ¬ z e i c h n e t, daß die Gesamtwandstärke (21) zwischen der äußeren Mantelfläche (5) und der inneren Wandfläche (4) des Bremskolbens (1) ungefähr gleich der Summe aus der Tiefe der inneren Ringnut (6) und der Tiefe der äußeren Ringnut (7) ist. 3. Brake piston according to claim 2, characterized in that the total wall thickness (21) between the outer lateral surface (5) and the inner wall surface (4) of the brake piston (1) is approximately equal to the sum of the depth of the inner annular groove (6) and the depth of the outer annular groove (7).
4. Bremskolben nach Anspruch 3, dadurch g e k e n n ¬ z e i c h n e t, daß die Tiefe der inneren Ringnut (6) ungefähr gleich der Tiefe der äußeren Ringnut (7) ist.4. Brake piston according to claim 3, characterized in that the depth of the inner annular groove (6) is approximately equal to the depth of the outer annular groove (7).
5. Bremskolben nach Anspruch 4, dadurch g e k e n ¬ z e i c h n e t, daß der kleinste Abstand (22) zwischen einer Wand der inneren Ringnut (6) und einer Wand der äußeren Ringnut (7) mindestens gleich oder größer als die verminderte Wandstärke (20) des Bremskolbens (1) ist,5. Brake piston according to claim 4, characterized in that the smallest distance (22) between a wall of the inner annular groove (6) and a wall of the outer annular groove (7) is at least equal to or greater than the reduced wall thickness (20) of the brake piston (1) is
6. Bremskolben nach Anspruch 5, dadurch g e k e n n ¬ z e i c h n e t, daß die innere Ringnut (6) einen im we¬ sentlichen trapezförmigen Querschnitt aufweist, der von einem zur Kolbenachse parallelen Nutboden (23) und zwei Nutflanken (24, 25) gebildet wird, wobei die dem offenen Ende des Bremskolbens (1) nächstliegende Nutflanke (25) senkrecht zur Kolbenachse und die andere Nutflanke (24) schräg dazu angeordnet ist.6. Brake piston according to claim 5, characterized in that the inner annular groove (6) has an essentially trapezoidal cross-section which is formed by a groove base (23) parallel to the piston axis and two groove flanks (24, 25), wherein the groove flank (25) closest to the open end of the brake piston (1) is arranged perpendicular to the piston axis and the other groove flank (24) is arranged obliquely thereto.
7. Scheibenbremse mit einem Bremskolben nach einem der An¬ sprüche 2 bis 6, dadurch g e k e n n z e i c h n e t, daß die zum Eingriff in die näher am Kolbenboden (2) an¬ geordnete innere Ringnut (6) mit längeren Federzungen (12, 13) versehene Haltefeder (11) eines am Bremskolben (1) anliegenden Bremsbelags (9) durch eine zusätzliche Einformung versteift ist.7. Disc brake with a brake piston according to one of claims 2 to 6, characterized in that the inner ring groove (6) arranged to engage in the closer to the piston head (2) is provided with longer spring tongues (12, 13) retaining spring ( 11) of a brake lining (9) resting on the brake piston (1) is stiffened by an additional molding.
8. Scheibenbremse nach Anspruch 7, dadurch g e k e n n ¬ z e i c h n e t, daß ein zwischen zwei gegenüberliegen¬ den Federzungen (12, 13) verlaufender Rand (27) der Hal¬ tefeder (11) durch Umbiegen versteift ist. 8. Disc brake according to claim 7, characterized in that one between two opposite spring tongues (12, 13) extending edge (27) of the retaining spring (11) is stiffened by bending.
9. Scheibenbremse nach Anspruch 7, dadurch g e k e n n ¬ z e i c h n e t, daß der Bereich zwischen zwei gegen¬ überliegenden Federzungen (12, 13) durch eingeprägte Sicken (28, 29) versteift ist.9. Disc brake according to claim 7, characterized in that the area between two opposite spring tongues (12, 13) is stiffened by embossed beads (28, 29).
10. Scheibenbremse nach einem der Ansprüche 7 bis 9, dadurch g e k e n n z e i c h n e t, daß die genannten Federzun¬ gen (12, 13) an einer die innere Ringnut (6) gegen die innere Wandfläche (4) des Bremskolbens (1) abgrenzenden Kante (26) anliegen und eine axiale Kraftkomponente er¬ zeugen, die den Bremsbelag (9) in Anlage am Bremskolben (1) hält.10. Disc brake according to one of claims 7 to 9, characterized in that said Federzun¬ gene (12, 13) on an inner ring groove (6) against the inner wall surface (4) of the brake piston (1) delimiting edge (26) apply and generate an axial force component that holds the brake lining (9) in contact with the brake piston (1).
11. Haltefeder für einen Bremsbelag mit den kennzeichnenden Merkmalen von einem der Ansprüche 7 bis 9.11. Retaining spring for a brake pad with the characterizing features of one of claims 7 to 9.
12. Bremsbelag mit Haltefeder nach Anspruch 11. 12. Brake pad with retaining spring according to claim 11.
PCT/EP1994/003827 1993-11-27 1994-11-18 Brake plunger for disk brakes WO1995014869A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP95900762A EP0729552A1 (en) 1993-11-27 1994-11-18 Brake plunger for disk brakes

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19934340453 DE4340453A1 (en) 1993-11-27 1993-11-27 Brake pistons for disc brakes
DEP4340453.7 1993-11-27

Publications (1)

Publication Number Publication Date
WO1995014869A1 true WO1995014869A1 (en) 1995-06-01

Family

ID=6503598

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1994/003827 WO1995014869A1 (en) 1993-11-27 1994-11-18 Brake plunger for disk brakes

Country Status (3)

Country Link
EP (1) EP0729552A1 (en)
DE (1) DE4340453A1 (en)
WO (1) WO1995014869A1 (en)

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WO2001077547A1 (en) * 2000-04-12 2001-10-18 Sinkhron-Rus, Obschestvo S Ogranichennoi Otvetstvennostiju Disc brake piston embodied by drawing

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DE19534220A1 (en) * 1995-09-15 1997-03-20 Teves Gmbh Alfred Brake piston
DE19537928A1 (en) * 1995-10-12 1997-04-17 Teves Gmbh Alfred Automobile disc brake using spring-fitted brake pads
DE19603586A1 (en) * 1996-02-01 1997-08-07 Teves Gmbh Alfred Cold-formed piston for a hydraulic brake
DE102017207140A1 (en) 2016-06-16 2017-12-21 Continental Teves Ag & Co. Ohg Steel brake piston for a hydraulic brake and method of manufacture
DE102017220789B4 (en) 2017-07-28 2023-08-10 Continental Automotive Technologies GmbH Friction pad retaining spring for improved brake piston fixation

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GB2086531A (en) * 1980-10-31 1982-05-12 Hooker Chemicals Plastics Corp Improved piston for disc brakes
EP0341392A1 (en) * 1988-05-07 1989-11-15 ALFRED TEVES GmbH Spot-type disc brake
EP0411814A2 (en) * 1989-08-04 1991-02-06 Lucas Industries Public Limited Company Improvements in or relating to disc brakes
WO1992018785A1 (en) * 1991-04-20 1992-10-29 Alfred Teves Gmbh Brake shoe with retaining spring

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DE3933395A1 (en) * 1989-10-06 1991-04-18 Teves Gmbh Alfred PARTIAL PAD DISC BRAKE
DE4215279A1 (en) * 1992-05-09 1993-11-11 Teves Gmbh Alfred Disc brake with operating piston displaceable with wear on brake blocks - has brake operating cylinder running into cooling fluid storage chamber which is enclosed by cooling ribs

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Publication number Priority date Publication date Assignee Title
GB2086531A (en) * 1980-10-31 1982-05-12 Hooker Chemicals Plastics Corp Improved piston for disc brakes
EP0341392A1 (en) * 1988-05-07 1989-11-15 ALFRED TEVES GmbH Spot-type disc brake
EP0411814A2 (en) * 1989-08-04 1991-02-06 Lucas Industries Public Limited Company Improvements in or relating to disc brakes
WO1992018785A1 (en) * 1991-04-20 1992-10-29 Alfred Teves Gmbh Brake shoe with retaining spring

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001077547A1 (en) * 2000-04-12 2001-10-18 Sinkhron-Rus, Obschestvo S Ogranichennoi Otvetstvennostiju Disc brake piston embodied by drawing

Also Published As

Publication number Publication date
EP0729552A1 (en) 1996-09-04
DE4340453A1 (en) 1995-06-01

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