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WO1992017713A1 - Frein a disque a garniture partielle et a etrier fixe - Google Patents

Frein a disque a garniture partielle et a etrier fixe Download PDF

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Publication number
WO1992017713A1
WO1992017713A1 PCT/EP1992/000719 EP9200719W WO9217713A1 WO 1992017713 A1 WO1992017713 A1 WO 1992017713A1 EP 9200719 W EP9200719 W EP 9200719W WO 9217713 A1 WO9217713 A1 WO 9217713A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
brake disc
carrier plate
disc
pads
Prior art date
Application number
PCT/EP1992/000719
Other languages
German (de)
English (en)
Inventor
Rolf Weiler
Uwe Bach
Uwe Hendrich
Florian Schubert
Original Assignee
Alfred Teves 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
Priority claimed from DE19914110869 external-priority patent/DE4110869C2/de
Priority claimed from DE19914115064 external-priority patent/DE4115064C2/de
Priority claimed from DE19914133486 external-priority patent/DE4133486C2/de
Application filed by Alfred Teves Gmbh filed Critical Alfred Teves Gmbh
Publication of WO1992017713A1 publication Critical patent/WO1992017713A1/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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/228—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a separate actuating member for each side
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • F16D65/0973—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces
    • F16D65/0974—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces acting on or in the vicinity of the pad rim in a direction substantially transverse to the brake disc axis
    • F16D65/0975—Springs made from wire
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0075—Constructional features of axially engaged brakes
    • F16D2055/0091—Plural actuators arranged side by side on the same side of the rotor

Definitions

  • the invention relates to a fixed-caliper partial brake disk with radially removable brake pads, according to the preamble of claim 1.
  • Disc brakes of the generic type are known, for example, from the Brake Manual / Bartsch-Verlag, Ottobrunn near Kunststoff, 9th edition, pages 145 to 148.
  • two brake pads are arranged in a radial shaft of the fixed calliper and secured against falling out by means of retaining pins. Used brake pads can easily be replaced with new ones by simply loosening the retaining pins and removing the brake pads radially from the shaft.
  • the circumferential forces that occur during braking are transmitted from the brake pads to the fixed caliper via guide surfaces arranged in the circumferential direction. The brake pads are always pressed against the guide disc outlet side.
  • Disc brakes with "drawn” brake shoes which are predominantly or exclusively supported on the brake disc inlet side of the brake carrier, have the advantage that they do not or at least have a much lower tendency to generate noise.
  • the object of the invention is to support the brake shoes of a fixed caliper brake of the generic type on the brake disk inlet side, without sacrificing the radial removal option.
  • the brake shoes consist of a carrier plate and one or more brake pads releasably attached to the carrier plate.
  • the carrier plates are provided with projections which cooperate with axial webs of the fixed caliper in such a way that the circumferential forces which occur during braking are be transferred to the fixed saddle.
  • This has the advantage of a low tendency to generate noise. If the friction linings are worn, the brake pads are loosened from the carrier plate and removed through a radial shaft of the fixed calliper. The assembly effort required for this is advantageously low.
  • the carrier plate does not have to be removed. After a single assembly, it always remains in the fixed saddle.
  • the brake pads are expediently constructed according to claim 2 from a simple back plate and a friction lining.
  • the brake pad can then be attached to the backing plate with its back plate.
  • the back plate can, according to claim 3, be significantly weaker than the carrier plate. This reduces the weight and manufacturing costs of the brake shoe and fixed calliper. The costs resulting from the replacement of worn brake pads are minimized by the arrangement of two brake pads disclosed in claim 4, which can then be particularly small and simple.
  • the clamp fastening of the carrier plates to the brake piston according to claim 6 ensures that they are taken away by the retracting brake piston after braking and an air gap between the friction linings and the brake disc is actively set.
  • the brake pads are radially insertable and thus particularly easy to assemble.
  • the known and proven arrangements described in claims 8 and 9 can be used in this embodiment.
  • the carrier plate has windows for receiving and securely holding the brake pads.
  • the carrier plate is particularly light and the brake pistons can act directly on the brake pads.
  • a leaf spring is provided according to claim 11, which advantageously also serves to secure the brake shoe to the brake piston.
  • a particularly simple and expedient embodiment of the leaf spring results from claim 12.
  • the leaf spring is releasably clamped to the radial edges of the brake shoe, which are easily accessible for the installer.
  • the arrangement disclosed in claim 13 ensures that the brake piston rests directly on the brake pad and prevents the leaf springs from slipping on the carrier plate.
  • the fixed caliper will be made of gray cast iron and the webs provided for guiding the brake shoes will be cast in one piece with the brake housing.
  • the webs then inevitably consist of the same material as the brake housing. However, they are heavily loaded by the circumferential forces that occur when braking and are exposed to corrosion. If the fixed caliper is cast for constructional reasons from a non-high-strength or non-corrosion-resistant material, the webs can be looked at. lent abrasion, corrosion and resilience functional defects occur.
  • the bolts according to the invention are made of a high-strength material and therefore have the advantage that they are strong and have little abrasion, without the fixed caliper itself having to be made of such a material.
  • the fixed caliper can consist of light metal, whereby the weight of the brake is considerably reduced.
  • the fixed caliper is made of cast aluminum and the bolts are made of stainless steel, whereby corrosion is practically excluded.
  • the brake shoe guides be designed in accordance with one of claims 18 to 20.
  • the distance between the lugs and the surfaces of the bolts, according to claim 20, enables small relative movements by means of which the brake shoe guides can free themselves of adhering corrosion products.
  • a further advantageous embodiment of the invention results from the features of patent claim 21.
  • the webs are integrated into the bridge sections of the brake housing which overlap the edge of the brake disc, the support surfaces for the brake shoes on the outer sides of the brake disc in the circumferential direction of the brake disc Bridge sections are arranged.
  • This configuration has the advantage that the shape of the brake housing is simplified and that the finishing of the support surfaces located on the outermost edge of the brake housing is facilitated.
  • the machining tool has free access to the point to be machined, so that no clearance must be provided for the tool in the brake housing for finishing, which would impair the rigidity of the bridge sections.
  • the bridge sections are even reinforced by the integrated webs.
  • the machining of the support surfaces becomes even easier.
  • the steps, together with support plates designed according to claim 23, enable the brake shoes to be secured and guided against being lifted out, which can be further improved by an arrangement according to the features of claim 24. »With this arrangement, there are no tipping moments due to friction, which could cause the brake shoe to lift out.
  • a leaf spring according to claim 25 is recommended.
  • the carrier plate For simple and detachable fastening of the brake pad to the carrier plate, it is advisable to design the carrier plate with a through-hole according to claim 26, preferably in conjunction with a U-shaped recess of the brake block according to claim 27 and a hold-down spring according to claim 28.
  • a preferred one and simple embodiment of the hold-down spring results from the features of claim 29.
  • the brake pad is inserted through the shaft of the brake housing, which is open to the outside, until it rests with its U-shaped recess on the projecting passage on the front of the carrier plate.
  • the hold-down spring is already locked captively with its two free ends in two openings in the brake pad back plate.
  • the fitter only needs to snap the bow-shaped central section of the spring into a further passage on the back of the carrier plate.
  • Claim 31 is also intended to provide protection for a correspondingly designed brake pad for use in a partial brake disc brake according to the invention. The same applies to a hold-down spring according to claim 32.
  • Figure 1 is a schematic diagram of a four-cylinder fixed-caliper partial brake disc brake, the right half of which is shown cut in the plane of the brake disc;
  • Figure 2 is a plan view of a brake shoe in a first embodiment;
  • FIG. 3 shows a side view in direction A of FIG. 2 of the same brake shoe with the brake pads removed;
  • FIG. 4 shows a detail B from FIG. 3 in section
  • FIG. 5 shows another configuration option for area B from FIG. 3;
  • FIG. 6 shows a plan view of a brake shoe in a second embodiment with the brake pads removed
  • FIG. 7 shows a section according to C-C from FIG. 6 with the brake pad fitted
  • Figure 8 is a leaf spring in a side view
  • FIG. 9 shows a leaf spring in a plan view in direction D from FIG. 8;
  • FIG. 10 shows a section along line E-E from FIG. 9;
  • Figure 11 shows a brake piston
  • FIG. 12 shows another view of the same brake piston in direction F from FIG. 11;
  • FIG. 13 shows a view of the inside of one half of a fixed saddle (the other half is designed with mirror symmetry) in a further embodiment;
  • FIG. 14 shows an enlarged detail G from FIG. 13;
  • FIG. 15 shows a section along line H-H from FIG. 13;
  • Figure 16 is a partial view of the inside of a fixed saddle in a further embodiment (the left half is mirror-symmetrical);
  • FIG. 17 shows a section through a brake shoe according to line J-J of FIG. 16.
  • a caliper housing 1 of a four-cylinder fixed-caliper partial brake disc brake is shown partially cut away.
  • the caliper housing 1 has a radial shaft 2 and two brake cylinders 3 on each axial side, in which brake pistons 4 slide axially.
  • two brake shoes 5, 6 are axially displaceably arranged, each having a carrier plate 7, 8, each with two L-shaped projections 9.
  • the saddle housing 1 is equipped with axially extending webs 10, 10 ', which have support surfaces 11, 11', 12, 12 'for the abutment of the projections 9.
  • the projections 9 engage behind the webs 10, 10 ', so that the circumferential forces which occur during braking are transmitted from the brake shoes 5, 6 via the projections 9 to the web 10, 10' on the brake disk inlet side.
  • the brake shoe 5, 6 pulls on its projection 9 on the brake disk inlet side, which bears against the support surface 12 for the transmission of the peripheral force.
  • FIGS. 1 A first exemplary embodiment of a brake shoe 5, 6 according to the invention is shown in FIGS.
  • two brake pads 13 are releasably attached on the L-shaped projections 9 provided support plate 7, 8 .
  • Every brake pad 13 consists of a back plate 14, which is about half as thick as the carrier plate 7, 8, and a friction lining 15 fastened on the back plate 14.
  • the back plate 14 has a section 16 free of friction lining, which has an opening 17 for opening Passage of a retaining pin 18 is provided.
  • the brake pads 13 are received in two recesses 19 of the carrier plate 7, 8, the depth of which corresponds to the thickness of the back plates 14.
  • the carrier plate 7, 8 is provided with passages 20 which encompass the back plates 14 laterally (FIG. 4) in order to prevent the brake pads 13 from falling axially out of the carrier plate 7, 8.
  • the retaining pins 18 releasably attached to the caliper housing 1 are removed and the brake pads 13 are pulled out of their carrier plates 7, 8 in the radial direction through the radial shaft 2 of the caliper housing 1.
  • the assembly of new brake pads is just as easy in reverse order.
  • Two leaf springs 21 are riveted to the support plate 1, 8 on the brake piston side, each having three spring arms 22.
  • the spring arms extend into the hollow brake pistons 4 with which they are in clamping engagement.
  • the carrier plate 7, 8 is tied to the brake pistons 4, so that the brake shoes 5, 6 are taken along by the retracting brake pistons 4 after braking and an air gap between the friction linings 15 and the brake disc is actively adjusted.
  • FIG. 7 Another design option for the carrier plate 7, 8 to improve the lateral guidance for the brake pads 13 is shown in FIG.
  • the carrier plate 7, 8 is here provided with passages 23 against which the back plates 14 of the brake pads 13 lie laterally in order to transmit the peripheral forces.
  • FIGS. 6 and 7 A second exemplary embodiment of a brake shoe 5, 6 according to the invention is shown in FIGS. 6 and 7.
  • the carrier plate 7, 8 here has two windows 26 which are provided with steps 25 at their edges 24.
  • the brake pads 27 are designed here with respect to their back plates 28 even more easily than in the first embodiment. They are inserted axially into the windows 26 of the carrier plate 1, 8 from the brake piston side and rest with their back plates 28 on the steps 25 which, together with special leaf springs 29, prevent the brake pads 27 from falling out of the windows 26.
  • FIGS. 8 to 10 show a leaf spring 29 designed according to the invention for a brake shoe 5, 6 according to the second exemplary embodiment.
  • the leaf spring 29 stamped and formed from a piece of spring sheet metal has a central section 30, from the center of which two clamping tongues 31 are punched out and bent almost perpendicular to section 30.
  • the clamping tongues 31 are intended for engagement in an inner annular groove 32 of the hollow brake cylinder 4.
  • the central section 30 merges at its two ends into two anchoring tongues 33, which are intended for anchoring the leaf spring 29 on the carrier plate 7, 8.
  • the carrier plate 7, 8 has steps 34 on its radially outer edges, which are encompassed by lugs 35 of the anchoring tongues 33.
  • the anchoring tongues 33 are provided with tabs 36 projecting radially beyond the support plate 7, 8.
  • the brake shoe 5, 6 is bound to the brake piston 4 by the leaf spring 29.
  • the central section 30 presses axially from behind against the back plate 28 of the brake pad 27 and holds it in the window 26 of the carrier plate 7, 8.
  • the fitter presses axially against the radially protruding tabs 36.
  • the anchoring tongues 33 detach from the carrier plate 7, 8, which the fitter then pushes axially in the direction of the brake disc.
  • the brake pads 27 fall axially out of the windows 26 and can be removed radially from the radial shaft 2 of the fixed caliper 1.
  • the new brake pads 27 are again introduced through the shaft 2 and inserted into the windows 26. Then the fitter pushes the carrier plate 7, 8 axially in the direction of the brake piston 4 until it engages behind the lugs 35 of the leaf springs 29.
  • the brake pistons 4 are provided with grooves 37 on their end faces intended for pressing against the brake pads 27, through which the contact surfaces 38 are divided into two.
  • the brake pistons 4 lie with their contact surfaces 38 directly against the back plates 28, while the respective leaf spring 29 is received by the groove 37 with its central section 30. This arrangement prevents the leaf spring 29 from slipping.
  • the carrier plate 42 is provided with two projections 45 (only one is visible in the figures), by means of which the brake shoes 41 are guided axially displaceably on the fixed caliper 46.
  • the fixed caliper 46 is provided with four bolts 47, each of which has a first section 48 and a free, second section 49. The bolts 47 are pressed with their first section 48 into bores 50 of the saddle housing.
  • the second section 49 is provided with support surfaces 51, 52, against which a projection 45 rests axially.
  • the projections 45 are provided with lugs 53 which engage in axially extending recesses 54 in the bolts 47.
  • a small distance of approximately 1 mm is provided between the lugs 53 and the surfaces 55 of the recesses 54 in order to enable a relative movement, by means of which the surfaces 55 or the lugs 53 are cleaned of corrosion products.
  • part of a fixed caliper 61 can be seen with a shaft 62 which is open radially outwards and a bridge section 63 which overlaps the outer edge of the brake disk 69 indicated by dashed lines.
  • the brake shoe 64 is protruding a carrier plate 65 and a brake block 66 releasably attached to the carrier plate 65, which is composed of a back plate 67 and a friction lining 68.
  • the left half of the fixed saddle, not shown, is essentially mirror-symmetrical to the right half.
  • the carrier plate 65 has two hook-shaped projections 73 which protrude in the circumferential direction of the brake disk 69, the ends 74 of which are angled radially outward and are provided with contact surfaces 75 for contact with the support surfaces 71.
  • the ends 74 are again provided with angled lugs 76 which engage behind the steps 72 in order to prevent the brake shoe 64 from lifting out.
  • the fixed caliper 61 has four brake cylinders, not shown in the figures, two of which are arranged side by side on each side of the brake disk 69.
  • One of four brake pistons 77 which are axially displaceable in the brake cylinders is indicated in FIG. 16 by dashed lines.
  • Two leaf springs 78 are riveted to the support plate 65 on the brake piston side and engage with their spring tongues 79, 80 in the interior of the hollow brake pistons 77.
  • the spring plate 65 is prestressed in the radial direction 82 relative to the fixed caliper 61 by a spring tongue 80, so that the projections 73 are pressed against the side surfaces 81 of the bridge sections 63 facing the brake disc axis.
  • an extension 83 protruding from the carrier plate 65 in the direction of the brake disk 69 is provided, which is engaged in a U-shaped recess 84 of the brake pad 66.
  • the brake pad 66 is preloaded radially against the carrier plate 65 by means of a hold-down spring 85 in the opposite direction 82.
  • the hold-down spring 85 consists of a piece of spring wire and has an approximately U-shaped central section 86, from which two arms 87, 88 protrude in opposite directions.
  • the arms 87, 88 are offset from the plane defined by the central section 86 and connected to the central section 86 by connecting sections 89, 90.
  • the carrier plate 65 is provided on the brake piston side with a projecting passage 91 on which the Middle section 86 is engaged.
  • the hold-down spring 85 encompasses two projections 92, 93 of the back plate 67 of the brake pad 66, which protrude in the radial direction 82, the angled ends of the arms 87, 88 engaging in openings 94 of the projections 92, 93.
  • the carrier plate 65 is also provided on its side facing the brake disk 69 with two displays 95 which protrude from the carrier plate plane and are arranged directly next to the narrow sides 96 of the brake pad 66. The circumferential force occurring during braking is transmitted from the brake pad 66 to the carrier plate 65 via these exhibitions 95.
  • the support surfaces 71 of the bridge sections 63 are arranged in such a way that they are cut by a straight line 97 running through the center of friction of the brake pad 66 in the circumferential direction of the brake disk 69. In this arrangement, tilting moments caused by frictional forces, which could result in lifting the support plate 65, do not occur.

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

Abstract

Dans un frein à disque à garniture partielle et à étrier fixe, les segments de frein (5, 6, 41, 64) sont composés d'une plaque de support (7, 8, 42, 65) et de plaquettes de frein (13, 27, 44, 66) fixées de manière amovible sur la plaque de support (7, 8, 42, 65). Les plaques de support (7, 8, 42, 65) sont pourvues de protubérances (9, 45, 73) qui coopèrent avec des bandes axiales (10, 10', 47, 70) du boîtier (1, 46, 61) de l'étrier de sorte que pendant le freinage des forces périphériques ne soient transmises qu'au côté de guidage du disque de freinage du boîtier (1, 46, 61) de l'étrier. Les plaquettes usées (13, 27, 44, 66) du frein à disque peuvent être enlevées sans grande dépense à travers une fente radiale (2, 62) du boîtier (1, 46, 61) de l'étrier, après avoir été enlevées des plaques de support (7, 8, 42, 65). Les plaques de support (7, 8, 42, 65) restent toujours dans le boîtier (1, 46, 61) de l'étrier. Ce frein à étrier fixe allie le confort de segments étirés de freins (5, 6, 41, 64) à l'avantage que représentent des dépenses minimes de montage lors du remplacement des plaquettes (13, 27, 44, 66).
PCT/EP1992/000719 1991-04-04 1992-04-01 Frein a disque a garniture partielle et a etrier fixe WO1992017713A1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DEP4110869.8 1991-04-04
DE19914110869 DE4110869C2 (de) 1991-04-04 1991-04-04 Festsattel-Teilbelagscheibenbremse
DE19914115064 DE4115064C2 (de) 1991-04-04 1991-05-08 Festsattel-Teilbelagscheibenbremse
DEP4115064.3 1991-05-08
DE19914133486 DE4133486C2 (de) 1991-04-04 1991-10-09 Festsattel-Teilbelagscheibenbremse
DEP4133486.8 1991-10-09

Publications (1)

Publication Number Publication Date
WO1992017713A1 true WO1992017713A1 (fr) 1992-10-15

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Application Number Title Priority Date Filing Date
PCT/EP1992/000719 WO1992017713A1 (fr) 1991-04-04 1992-04-01 Frein a disque a garniture partielle et a etrier fixe

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Country Link
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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5588508A (en) * 1993-04-15 1996-12-31 Alliedsignal Europe Services Technique Disk brake using a pulled pad with permanent bearing
WO2006058591A1 (fr) * 2004-11-30 2006-06-08 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Frein a disque, en particulier pour un vehicule utilitaire
WO2011151235A1 (fr) * 2010-06-02 2011-12-08 Continental Teves Ag & Co. Ohg Frein à étrier fixe et garniture de frein pour un frein à étrier fixe
KR101317152B1 (ko) * 2009-11-30 2013-10-11 주식회사 만도 디스크 브레이크
EP2846060A1 (fr) * 2013-09-06 2015-03-11 Nissin Kogyo Co., Ltd. Frein à disque de véhicule
WO2015155708A1 (fr) 2014-04-08 2015-10-15 Freni Brembo S.P.A. Plaquette de frein à disque, ressort pour étrier de frein à disque et assemblage d'étrier de frein à disque
EP3574228B1 (fr) * 2017-01-26 2020-06-03 SAF-HOLLAND GmbH Mâchoire de frein, système d'assemblage modulaire d'une mâchoire de frein, dispositif de freinage et procédé de fabrication d'une mâchoire de freinage
DE102019000444A1 (de) 2019-01-22 2020-07-23 Zf Active Safety Gmbh Bremsbelaganordnung für eine Fahrzeugscheibenbremse
CN114165541A (zh) * 2021-12-20 2022-03-11 南方天合底盘系统有限公司 一种快换式制动系统

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2266053A1 (fr) * 1974-03-28 1975-10-24 Gen Motors France
EP0106782A1 (fr) * 1982-09-15 1984-04-25 Abex Corporation Plaquette segmentée pour freins à disque
FR2598762A1 (fr) * 1986-05-16 1987-11-20 Valeo Dispositif de freinage, par exemple pour une installation industrielle et plaquette de freinage adaptee a un tel dispositif
US4745992A (en) * 1987-05-29 1988-05-24 General Motors Corporation Brake shoe assembly retainer and lining wear sensor
DE4020077A1 (de) * 1990-06-23 1992-01-02 Teves Gmbh Alfred Bremssattel fuer scheibenbremsen
EP0341610B1 (fr) * 1988-05-07 1994-01-19 ITT Automotive Europe GmbH Frein à disque à garniture partielle

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2266053A1 (fr) * 1974-03-28 1975-10-24 Gen Motors France
EP0106782A1 (fr) * 1982-09-15 1984-04-25 Abex Corporation Plaquette segmentée pour freins à disque
FR2598762A1 (fr) * 1986-05-16 1987-11-20 Valeo Dispositif de freinage, par exemple pour une installation industrielle et plaquette de freinage adaptee a un tel dispositif
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Cited By (17)

* Cited by examiner, † Cited by third party
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US5588508A (en) * 1993-04-15 1996-12-31 Alliedsignal Europe Services Technique Disk brake using a pulled pad with permanent bearing
WO2006058591A1 (fr) * 2004-11-30 2006-06-08 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Frein a disque, en particulier pour un vehicule utilitaire
KR101317152B1 (ko) * 2009-11-30 2013-10-11 주식회사 만도 디스크 브레이크
US9365193B2 (en) 2010-06-02 2016-06-14 Continental Teves Ag & Co. Ohg Fixed caliper brake and brake pad for a fixed caliper brake
EP3104035B1 (fr) 2010-06-02 2019-08-28 Continental Teves AG & Co. OHG Garniture de frein pour freins a etrier
CN102918293A (zh) * 2010-06-02 2013-02-06 大陆-特韦斯贸易合伙股份公司及两合公司 固定钳式制动器和用于固定钳式制动器的制动衬件
JP2013531195A (ja) * 2010-06-02 2013-08-01 コンチネンタル・テベス・アーゲー・ウント・コンパニー・オーハーゲー 固定キャリパブレーキ及び固定キャリパ用ブレーキパッド
EP2577085B1 (fr) 2010-06-02 2017-01-25 Continental Teves AG & Co. oHG Frein à étrier fixe et garniture de frein pour un frein à étrier fixe
WO2011151235A1 (fr) * 2010-06-02 2011-12-08 Continental Teves Ag & Co. Ohg Frein à étrier fixe et garniture de frein pour un frein à étrier fixe
EP3104035A1 (fr) * 2010-06-02 2016-12-14 Continental Teves AG & Co. OHG Garniture de frein pour freins a etrier
US9377069B2 (en) 2013-09-06 2016-06-28 Nissin Kogyo Co., Ltd. Vehicle disc brake
EP2846060A1 (fr) * 2013-09-06 2015-03-11 Nissin Kogyo Co., Ltd. Frein à disque de véhicule
WO2015155708A1 (fr) 2014-04-08 2015-10-15 Freni Brembo S.P.A. Plaquette de frein à disque, ressort pour étrier de frein à disque et assemblage d'étrier de frein à disque
US10316912B2 (en) 2014-04-08 2019-06-11 Freni Brembo S.P.A. Disc brake pad, spring for disc brake caliper and disk brake caliper assembly
EP3574228B1 (fr) * 2017-01-26 2020-06-03 SAF-HOLLAND GmbH Mâchoire de frein, système d'assemblage modulaire d'une mâchoire de frein, dispositif de freinage et procédé de fabrication d'une mâchoire de freinage
DE102019000444A1 (de) 2019-01-22 2020-07-23 Zf Active Safety Gmbh Bremsbelaganordnung für eine Fahrzeugscheibenbremse
CN114165541A (zh) * 2021-12-20 2022-03-11 南方天合底盘系统有限公司 一种快换式制动系统

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