WO1995014869A1 - Piston pour freins a disque - Google Patents

Piston pour freins a disque 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)
English (en)
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/fr
Publication of WO1995014869A1 publication Critical patent/WO1995014869A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • F16D65/0973—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.

Landscapes

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

Abstract

Un piston (1) cupuliforme pour freins à disque comporte une rainure annulaire (6) intérieure destinée à recevoir un ressort de retenue (11) pour fixer une garniture de frein (9) et une rainure annulaire (7) extérieure pour fixer un capuchon de protection (18). Selon l'invention, la rainure intérieure (6) est déportée dans le sens axial par rapport à la rainure annulaire (7) extérieure, suffisamment pour empêcher que l'épaisseur (20) de la paroi du piston de frein (1), déjà réduite par une rainure annulaire (7), le soit encore davantage par la mise en place de l'autre rainure annulaire (6). L'épaisseur (20) de la paroi reste réduite pour que la force d'application du frein puisse être transmise à la garniture de frein (9), l'épaisseur totale (21) de la paroi du piston de frein (1) étant, quant à elle, avantageusement faible. Ce piston de frein (1) présente de ce fait l'avantage d'avoir un poids réduit tout en demeurant aussi performant.
PCT/EP1994/003827 1993-11-27 1994-11-18 Piston pour freins a disque WO1995014869A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP95900762A EP0729552A1 (fr) 1993-11-27 1994-11-18 Piston pour freins a disque

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP4340453.7 1993-11-27
DE19934340453 DE4340453A1 (de) 1993-11-27 1993-11-27 Bremskolben für Scheibenbremsen

Publications (1)

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

Family

ID=6503598

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1994/003827 WO1995014869A1 (fr) 1993-11-27 1994-11-18 Piston pour freins a disque

Country Status (3)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001077547A1 (fr) * 2000-04-12 2001-10-18 Sinkhron-Rus, Obschestvo S Ogranichennoi Otvetstvennostiju Piston de frein a disques fabrique par etirage

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19534220A1 (de) * 1995-09-15 1997-03-20 Teves Gmbh Alfred Bremskolben
DE19537928A1 (de) * 1995-10-12 1997-04-17 Teves Gmbh Alfred Kolben für eine Teilbelag-Scheibenbremse
DE19603586A1 (de) * 1996-02-01 1997-08-07 Teves Gmbh Alfred Kaltgeformter Kolben für eine hydraulische Bremse
DE102017207140A1 (de) 2016-06-16 2017-12-21 Continental Teves Ag & Co. Ohg Stahlbremskolben für eine hydraulische Bremse und Verfahren zur Herstellung
DE102017220789B4 (de) * 2017-07-28 2023-08-10 Continental Automotive Technologies GmbH Reibbelaghaltefeder zur verbesserten Bremskolbenfixierung

Citations (4)

* Cited by examiner, † Cited by third party
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 (fr) * 1988-05-07 1989-11-15 ALFRED TEVES GmbH Frein à disque à garniture partielle
EP0411814A2 (fr) * 1989-08-04 1991-02-06 Lucas Industries Public Limited Company Freins à disque
WO1992018785A1 (fr) * 1991-04-20 1992-10-29 Alfred Teves Gmbh Segment de frein a ressort de retenue

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3933395A1 (de) * 1989-10-06 1991-04-18 Teves Gmbh Alfred Teilbelag-scheibenbremse
DE4215279A1 (de) * 1992-05-09 1993-11-11 Teves Gmbh Alfred Scheibenbremse mit Speicherraum für Kühlflüssigkeit

Patent Citations (4)

* Cited by examiner, † Cited by third party
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 (fr) * 1988-05-07 1989-11-15 ALFRED TEVES GmbH Frein à disque à garniture partielle
EP0411814A2 (fr) * 1989-08-04 1991-02-06 Lucas Industries Public Limited Company Freins à disque
WO1992018785A1 (fr) * 1991-04-20 1992-10-29 Alfred Teves Gmbh Segment de frein a ressort de retenue

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001077547A1 (fr) * 2000-04-12 2001-10-18 Sinkhron-Rus, Obschestvo S Ogranichennoi Otvetstvennostiju Piston de frein a disques fabrique par etirage

Also Published As

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

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