GB2027826A - Disc brake assembly - Google Patents

Disc brake assembly Download PDF

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Publication number
GB2027826A
GB2027826A GB7922550A GB7922550A GB2027826A GB 2027826 A GB2027826 A GB 2027826A GB 7922550 A GB7922550 A GB 7922550A GB 7922550 A GB7922550 A GB 7922550A GB 2027826 A GB2027826 A GB 2027826A
Authority
GB
United Kingdom
Prior art keywords
disc
brake
carrier member
caliper
brake pad
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
GB7922550A
Other versions
GB2027826B (en
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF International UK Ltd
Original Assignee
Lucas Industries Ltd
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 Lucas Industries Ltd filed Critical Lucas Industries Ltd
Publication of GB2027826A publication Critical patent/GB2027826A/en
Application granted granted Critical
Publication of GB2027826B publication Critical patent/GB2027826B/en
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
    • F16D55/2265—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
    • F16D55/227—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing by two or more pins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
    • F16D55/2265—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0016—Brake calipers
    • 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
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/34—Mechanical mechanisms converting rotation to linear movement or vice versa acting in the direction of the axis of rotation
    • F16D2125/36—Helical cams, Ball-rotating ramps
    • 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
    • F16D69/00—Friction linings; Attachment thereof; Selection of coacting friction substances or surfaces

Landscapes

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

Abstract

A disc brake assembly (e.g. for motor-cycles), comprises a carrier member (2) mounted to the vehicle frame and a caliper member (4) mounted on the carrier member (2) for sliding non-rotative movement (by a non-circular pin (5) or by two bolts). Friction pads (23, 24) on opposite sides of disc 7 are of sintered material-pad (23) is applied by a mechanical cam actuator and pad (24) by reaction, and pad (24) is sintered directly to the caliper member (4). The pad (23) may also be sintered directly to a piston (21) or a sleeve (27-see Figs. 5,6). Various cam actuators are disclosed, operable by cables whose length may be adjusted. <IMAGE>

Description

SPECIFICATION Sintered pad brakes for light vehicles This invention relates to disc brakes, and more particularly to a disc brake assembly suitable for use on light vehicles, for example light motor cycles and mopeds.
Disc brakes for motor cars are well known, and in recent years disc brakes have been developed for use on motor cycles. Such disc brakes are either hydraulicaliy or mechanically operated, hydraulic operation having the advantage that the brake is self-adjusting, i.e.
brake pad wear is automatically compensated for by the addition of hydraulic fluid to the hydraulic system from a reservoir.
Whilst hydraulically actuated disc brakes for motor cycles have proved highly successful in use, they do have the disadvantage that they are expensive to manufacture since the master cylinder and the slave cylinder must be machined and finished to a high degree of accuracy. In addition, a hydraulic reservoir must be provided to keep the hydraulic system topped up as the brake pads wear, and this adds to the expense and the bulk of the hydraulic system. Accordingly, known hydraulically operated disc brakes are not suitable for small light motor cycles and mopeds since they are too large and too expensive.
In known mechanically operated disc brakes adjusting means are provided to compensate for pad wear. Known adjusting means which automatically compensate for pad wear are complex, and accordingly expensive, and this again renders such brakes impractical for use on light motor cycles requiring a low-cost braking system.
According to one feature of the present invention there is provided a disc brake assembly comprising: a carrier member for mounting on a vehicle frame adjacent a brake disc; a caliper member mounted on the carrier member for sliding movement relative thereto in a direction parallel to the axis of rotation of the disc; a first brake pad mounted on the caliper member for engaging one side of the brake disc; a second brake pad for engaging the other side of the brake disc; and force means for forcing the second brake pad into engagement with the brake disc and forcing the caliper member to slide relative to the carrier member to bring the first brake pad into engagement with the brake disc, wherein the brake pads each comprise a thin layer of wear resistant sintered material, the first brake pad being sintered directly to the caliper member.
Preferably, the second brake pad is sintered directly to a piston member slidably mounted in the carrier member, the face of the piston member remote from the brake pad being acted upon by the force means to apply the second brake pad to the disc.
The use of a sintered pad material provides a disc brake assembly in which very little wear will occur to the pads in use. Thus, the need for an adjusting mechanism capable of compensating for pad wear is obviated, and the force means may comprise a simple mechanical actuator. The coefficient of friction of such sintered materials is sufficiently high to provide adequate braking force for a light vehicle, for example a light motor cycle. Accordingly, an embodiment of the invention provides a low cost mechanically actuated disc brake assembly suitable for a light vehicle, for example a light motor cycle or moped.
Preferably, the caliper member is mounted on the carrier member for sliding movement by a non-circular pin to prevent rotation of the caliper member relative to the carrier member and thereby permit torque forces applied to the first brake pad in use to be transferred to the vehicle frame via the caliper member, the pin and the carrier member.
The second brake pad is preferably slidably mounted on the carrier member so that torque forces applied to the second brake pad in use are transferred directly to the carrier member for transfer to the vehicle frame.
The provision of a non-rotative coupling between the caliper member and the carrier member enables the torque forces applied to the first brake pad to be transmitted to the frame of the vehicle via the caliper member.
Accordingly, the carrier member can be located entirely on one side of the disc, reducing the cost of the carrier member and ensuring that the minimum of space is required on the side of the disc remote from the carrier member. A single non-circular pin provides the necessary non-rotative connection at low cost, rendering the structure suitable for light inexpensive vehicles.
The above and further features and advantages of the invention will become clear from the following description of embodiments thereof, given by way of example only, reference being had to the accompanying drawings wherein: Figure 1 is a side view of a disc brake assembly, viewed from the wheel side of the assembly, the disc being indicated in broken lines; Figure 2 is a side view of the assembly of Fig. 1 from the other side; Figure 3 is a cross sectional view of the assembly of Figs. 1 and 2, details of the actuating mechanism being omitted in the interests of clarity; Figure 4 is a detailed sectional view of the actuating mechanism of the assembly of Figs.
1-3; Figures 5 and 6 are respectively a side view and a section of another embodiment; Figures 7 and 8 are respectively a side view and a part-sectional end view of a further embodiment; and Figure 9 is a sectional view, similar to Fig.
3, of yet another embodiment.
Referring to Figs. 1-4 of the drawings, the disc brake assembly 1 comprises a carrier member 2 provided with lugs 3 by which, in use, it is mounted on the frame of a vehicle, for example on the front forks of a light motor cycle. A caliper member 4 is slidably mounted on the carrier member 2 by means of a pin 5.
The pin 5 is non-circular in transverse crosssection and is slidably mounted in a complementary bearing portion 6 of the carrier member for sliding movement in a direction parallel to the axis of rotation of the disc 7 provided for the disc brake assembly. Rubber seals 8 prevent the ingress of dirt and moisture to the sliding connection between the pin 5 and the bearing portion 6 of the carrier member.
The caliper member 4 comprises a first portion 9 which spans the bearing portion 6, and a second portion 10 rigidly secured to the first portion 9 by means of a nut 11 mounted on the end of the pin 5. The apertures in the first portion 9 and the second portion 10 of the caliper member through which the pin 5 passes have a transverse cross-section complementary to the non-circular cross-section of the pin 5, and accordingly the caliper member is non-rotatively mounted on the pin 5. The non-rotative connection between the pin 5 and the caliper member, in combination with the non-rotative sliding connection between the pin 5 and the bearing portion 6 means that the caliper member can slide relative to the carrier member in a direction parallel to the axis of rotation of the disc 7, but cannot rotate relative to the carrier member.
A pivot pin 1 2 is secured to the first portion 9 of the caliper member and provides a support upon which an operating arm 1 3 is rotatively mounted. The portion of the operating arm 1 3 surrounding the pivot pin 1 2 is formed with a helical cam surface 14 (Fig. 4) which engages a complementary cam surface 1 5 formed on the first portion 9 of the caliper member. Details of the profile of the cam surfaces have been omitted from Fig. 3 in the interests of clarity. A lever portion 1 6 of the operating arm extends from the portion of the operating arm surrounding the pivot pin and terminates in a connection 1 7 for receiving the end of an operating cable.The caliper member 4 is provided with a lug 18 for receiving the sheath of an operating cable, and the arrangement is such that rotation of the operating arm 1 3 about the pivot pin 1 2 towards the lug 18 causes the cam surfaces 14 and 1 5 to operate to move the portion of the operating lever surrounding the pivot pin towards the disc 7. Such movement of the operating arm compresses Belleville washers 1 9 against a clip 20 secured to the end of pivot pin 12. The compressed Belleville washers 1 9 provide a force tending to return the cam surfaces to their original relative positions, and accordingly when the operating cable is released the operating arm returns to its initial position as shown in Fig. 2.
The side of the operating arm 1 3 remote from the cam surface 1 5 is slidably engaged by a piston 21 which is slidably mounted in a bore 22 in the carrier member. The end of the piston 21 remote from the operating arm 1 3 is provided with a friction lining 23 for frictionally engaging the surface of the disc 7.
The portion of the caliper member 4 facing the piston 21 is provided with a second friction lining 24 for engaging the opposite side of the disc 7.
In operation, rotation of the operating arm 1 3 towards the lug 1 8 causes the cam surface 14 to move up the cam surface 1 5 and towards the disc 7. This action advances the piston 21 towards the disc 7 until the friction lining 23 engages the disc. This engagement produces a reaction force which is transmitted via the piston 21 and arm 23 to the caliper member 4 and causes the caliper member 4 and pin 5 to slide in the bearing portion 6 of the carrier member to bring the friction lining 24 into engagement with the disc 7. A braking force is accordingly produced. The torque force produced on the friction lining 23 in use is transmitted to the piston 21 and from the piston 21 directly to the carrier member 2.
The torque force produced on the friction lining 24 is transmitted to the caliper member 4 and from the caliper member 4 by way of the non-rotative connection provided by the pin 5 to the carrier member 2. The friction linings 23, 24 are sintered directly to the piston 21 and the caliper 4 respectively and are of sintered friction material, for example Jurid SL/20080/30/0.
Such sintered friction materials may have a coefficient of friction which is low relative to that of conventional friction lining materials.
However, since the vehicle upon which the brake assembly 1 is fitted is a light vehicle, the braking force produced is adequate. The sintered friction material is, however, very hard and very little wear of the friction material will occur in use. Accordingly, no provision need be made for adjusting the clearance between the friction linings and the disc in use. In accordance with the usual practice, of course, it will be desirable to provide for adjustment of the effective length of the cable to take account of stretching of the cable in use. Such adjustment can be provided by any convenient means, for example a screw adjustment on the outer sheath of the cable at the lug 1 8.
A rubber seal 25 is provided surrounding the inner end of the operating arm 1 3 to protect the cam surfaces from the ingress of dirt and moisture.
Referring now to Figs. 5 and 6 an alternative embodiment of the invention is shown.
In the alternative embodiment, the operating arm 1 3 is provided with a helical cam surface which cooperates with the complementary cam surface on the caliper member as described above with reference to the embodiment of Figs. 1-4. However, in the case of the embodiment of Figs. 5 and 6 the operating arm is rotatably mounted on a pivot pin 1 2A which extends slidably through an aperture in the caliper member. The pivot pin is provided with an enlarged head 26 which engages the face of the operating arm 1 3 remote from the cam surfaces. Belleville washers 1 9A are located between an abutment surface provided by the caliper member and a clip 20A to bias the pivot pin to the right as viewed in Fig. 6, i.e. away from the disc.
Rotation of the operating arm 1 3 towards the lug18 causes the cam surfaces of the operating arm and the caliper member to engage and move the enlarged head 26 of the pivot pin towards the disc, compressing the Belleville washers 1 9A. When the operating arm 1 3 is released, the Belleville washers 1 9A cause the cam surfaces to move back to their original relative positions, returning the operating lever to its initial position.
The friction lining 23A is substantially identical to the friction lining 23 of the embodiment of Figs. 1-4, but is sintered to a sleeve 27 slidably mounted in a bore in the carrier member, rather than to the piston 21. The enlarged head 26 of the pivot pin is received in the sleeve 27 for applying the braking force to the sleeve 27.
It will also be noted in Fig. 6 that a locating pin 28 extends between the second portions of the caliper member to assist in preventing relative rotation of the two portions of the caliper member.
In another modification, illustrated in Figs.
7 and 8, the sliding connection between the carrier member and the caliper member is provided by two bolts 29 which hold together with two portions 9,10 of the caliper member, and slide in respective bearing portions in the carrier member. It will be appreciated that the two-bolt arrangement of Figs. 7 and 8 could replace the single-pin arrangement of any of the other embodiments.
In Fig. 9 there is illustrated a brake similar to that of Figs. 1 to 4 and the same reference numerals have been used to denote corresponding parts. Fig. 9 shows a modification which overcomes a problem which may be encountered with the embodiment of Figs. 1 to 4, namely that the piston 21 may rotate during actuation of the arm 1 3. To overcome this problem there is provided between the piston 21 and arm 1 3 an intermediate cupshaped member 31 having a radially outwardly directed flange 31A which extends between the arm 1 3 and one end of the seal 25. The central portion of the base of member 31 engages a boss 32 formed on the piston 21. The friction of engagement between the intermediate member 31 and the seal 25 and piston 21 is such that the intermediate member 31 can rotate relative to the piston 21 upon actuation of the arm 1 3 and thus rotation of piston 21 cannot occur.
It will be appreciated that in the embodiment of Figs. 5 and 6, the head 26 performs a function similar to the member 31 of Fig. 9, and can rotate relative to piston 27.

Claims (10)

1. A disc brake assembly comprising: a carrier member for mounting on a vehicle frame adjacent a brake disc; a caliper member mounted on the carrier member for sliding movement relative thereto in a direction parallel to the axis of rotation of the disc; a first brake pad mounted on the caliper member for engaging one side of the brake disc; a second brake pad for engaging the other side of the brake disc; and force means for forcing the second brake pad into engagement with the brake disc and forcing the caliper member to slide relative to the carrier member to bring the first brake pad into engagement with the brake disc, wherein the brake pads each comprise a thin layer of wear resistant sintered material, the first brake pad being sintered directly to the caliper member.
2. A disc brake assembly according to claim 1 wherein the second brake pad is sintered directly to a piston member slidably mounted in the carrier member, the face of the piston member remote from the brake pad being acted upon by the force means to apply the second brake pad to the disc.
3. A disc brake assembly according to claim 1 or claim 2 wherein the caliper member is mounted for sliding movement on the carrier member by a non-circular pin to prevent rotation of the caliper member relative to the carrier member.
4. A disc brake assembly according to claim 3 wherein the caliper member comprises a plurality of separate parts held together by the pin.
5. A disc brake assembly according to any preceding claim wherein the second brake pad is slidably mounted on the carrier member in such a manner that torque forces applied to the second brake pad in use are transferred directly to the carrier member.
6. A disc brake assembly according to any preceding claim wherein the force means is a mechanical actuator.
7. A disc brake assembly according to claim 6 wherein the mechanical actuator comprises a lever mounted between the carrier member and the second brake pad for rotation relative to the carrier member, the lever and the carrier member being formed with complementary cam surfaces which produce relative movement of the lever and the carrier member along the axis of rotation of lever when the lever is rotated.
8. A disc brake assembly according to claim 7 including biasing means biasing the cam surfaces towards each other.
9. A disc brake assembly according to claim 8 wherein the biasing means comprises at least one Belleville washer.
10. A disc brake assembly, substantially as hereinbefore described with reference to and as shown in the accompanying drawings.
GB7922550A 1978-06-29 1979-06-28 Disc brake assembly Expired GB2027826B (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB7828247 1978-06-29

Publications (2)

Publication Number Publication Date
GB2027826A true GB2027826A (en) 1980-02-27
GB2027826B GB2027826B (en) 1982-07-28

Family

ID=10498181

Family Applications (1)

Application Number Title Priority Date Filing Date
GB7922550A Expired GB2027826B (en) 1978-06-29 1979-06-28 Disc brake assembly

Country Status (6)

Country Link
JP (1) JPS5510197A (en)
AT (1) AT383880B (en)
DE (1) DE2926407A1 (en)
FR (1) FR2429931B1 (en)
GB (1) GB2027826B (en)
IT (1) IT1162456B (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9222532B2 (en) 2006-09-19 2015-12-29 Meritor Heavy Vehicle Braking Systems (Uk) Limited Brake carrier

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60244993A (en) * 1984-05-21 1985-12-04 シャープ株式会社 Display
JPS6163032U (en) * 1984-09-29 1986-04-28
DE3514497C2 (en) * 1985-04-22 1995-11-09 Teves Gmbh Alfred Protective sleeve for a pin guide of a partial-pad disc brake
EP3101301B2 (en) 2015-06-04 2024-03-06 Meritor Heavy Vehicle Braking Systems (UK) Limited Guide assembly
DE102017010104A1 (en) 2017-10-27 2018-12-13 Daimler Ag Floating caliper part disc brake and brake pad carrier for a floating caliper part disc brake

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3265167A (en) * 1964-07-10 1966-08-09 Goodyear Tire & Rubber Integral molded piston and lining for brakes and method for forming thereof
FR1527763A (en) * 1966-10-06 1968-06-07 Hispano Suiza Lallemant Soc Improvements to friction disc devices, in particular to brakes
FR1541124A (en) * 1967-08-25 1968-10-04 Jurid Werke Gmbh Friction disc for brakes and clutches
ZA712143B (en) * 1970-04-08 1971-12-29 Girling Ltd Improvements in disc brakes for vehicles
US3708040A (en) * 1970-08-19 1973-01-02 Kelsey Hayes Co Disk brake with servo action
JPS5316463B2 (en) * 1973-02-16 1978-06-01
JPS5316864B2 (en) * 1973-03-19 1978-06-03
JPS50127059A (en) * 1974-03-23 1975-10-06
JPS536927Y2 (en) * 1974-07-19 1978-02-22
JPS5817890B2 (en) * 1976-11-20 1983-04-09 トキコ株式会社 mechanical disc brake

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9222532B2 (en) 2006-09-19 2015-12-29 Meritor Heavy Vehicle Braking Systems (Uk) Limited Brake carrier

Also Published As

Publication number Publication date
JPS5510197A (en) 1980-01-24
FR2429931A1 (en) 1980-01-25
AT383880B (en) 1987-09-10
IT7949583A0 (en) 1979-06-28
GB2027826B (en) 1982-07-28
IT1162456B (en) 1987-04-01
FR2429931B1 (en) 1987-10-23
DE2926407A1 (en) 1980-01-10
ATA457979A (en) 1987-01-15

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PCNP Patent ceased through non-payment of renewal fee