GB1567005A - Disc brakes for vehicles - Google Patents

Disc brakes for vehicles Download PDF

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Publication number
GB1567005A
GB1567005A GB4650075A GB4650075A GB1567005A GB 1567005 A GB1567005 A GB 1567005A GB 4650075 A GB4650075 A GB 4650075A GB 4650075 A GB4650075 A GB 4650075A GB 1567005 A GB1567005 A GB 1567005A
Authority
GB
United Kingdom
Prior art keywords
draw
bar
groove
washer
disc brake
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
GB4650075A
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.)
Girling Ltd
Original Assignee
Girling 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 Girling Ltd filed Critical Girling Ltd
Priority to GB4650075A priority Critical patent/GB1567005A/en
Priority to US05/734,670 priority patent/US4051925A/en
Priority to JP51134005A priority patent/JPS5260380A/en
Priority to FR7633607A priority patent/FR2331715A1/en
Priority to SU762417312A priority patent/SU689606A3/en
Priority to BR7607518A priority patent/BR7607518A/en
Priority to IT7629183A priority patent/IT1064154B/en
Priority to DE19762651539 priority patent/DE2651539A1/en
Priority to ES453201A priority patent/ES453201A1/en
Publication of GB1567005A publication Critical patent/GB1567005A/en
Expired legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • 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
    • F16D55/22655—Constructional details of guide 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
    • 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
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0016—Brake calipers

Landscapes

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

Description

(54) IMPROVEMENTS IN DISC BRAKES FOR VEHICLES (71) We, GIRLING LIMITED, a British Company, of Kings Road, Tyseley, Birmingham, 11 do hereby declare the invention for which we pray that a patent may be granted to us and the method by which it is to be performed to be particularly described in and by the following state ment: - This invention relates to disc brakes for vehicles of the kind in which a first friction pad assembly is adapted to be urged directly mto engagement with one face of a rotatable disc by actuating means, and a second friction pad assembly is adapted to be applied indirectly to the opposite face of the disc by the reaction of the actuating means which is applied to the second friction pad assembly through a clamping member straddling a portion of the periphery of the disc and movable axially with respect to a relatively stationary carrier member, the clamping member comprising a yoke assembly consisting of a pair of pressure plates which are chordal to the disc and are located on opposite sides thereof, and circumferentially spaced draw-bars which interconnect the pressure plates at their outermost ends and determine the axial spacing between the pressure plates.
In one known disc brake of the kind set forth at least one end of each draw-bar is threaded and is screwed into a threaded blind bore of a nut until the threaded end engages with the base of the bore which defines a stop and means, for example split pins, are provided to lock the nut against rotation. The stops determine the effective lengths of bars between the pressure plates and hence set the spacing therebetween.
The opposite ends of the draw-bars may be formed with integral heads which bear on one of the pressure plates or, alternatively, the said opposite ends may also be screwthreaded and screwed into blind bores in one of the pressure plates.
The provision of blind threaded bores is an expensive operation and requires considerable skill particularly when the depth of a bore is to be controlled within close tolerances. A heading operation is also very expensive, particularly because the material which has to be used is of high strength.
In our British Patent Specification No. 1 193 641 a disc brake of the kind set forth is described, in which each draw bar is provided with an integral head at one end and a threaded portion at the other end, an open-ended nut being screwed onto the threaded end. Spherical joints are interposed between the draw-bars and the pressure plates. The working length of each bar is, in this case, individually adjusted and locked by means of lock nuts.
According to our invention in a disc brake of the kind set forth for vehicles each draw-bar is provided at at least one end with a screw-threaded portion, and a member in which that end of the draw-bar is connected has an open-ended screw-threaded bore into which the screw-threaded portion is screwed, a releasable coupling being provided between the said one end of each draw-bar and the member, and at least one of said couplings comprising an abutment member releasably retained in a groove defined in the member and engaged within a groove in the draw-bar located between the screw-threaded portion and an end portion at the said one end of the draw-bar.
Preferably the diameter of the end portion is less than the diameter of the screwthreaded portion so as to provide space for the abutment member.
The releasable coupling performs two functions namely defining a stop for the said one end of the draw-bar and preventing relative rotation between the member and the draw-bar taking place. Thus the construction is considerably simplified and elaborate machining to produce blind bores is eliminated.
The member may comprise one of the pressure plates or a nut screwed onto the end of a draw-bar which projects through a clearance bore in the other pressure plate.
Preferably screw-threaded portions are provided at both ends of each draw-bar so that one portion is screwed into an openended bore in one of the pressure plates and the other portion is passed through a clearance bore in the other pressure plate to receive a nut having an open-ended screwthreaded bore, releasable couplings being provided at both ends of each draw-bar, each coupling comprising an abutment member retained in a groove in one of the bores and engaged within a groove in the draw-bar located between the screwthreaded portion which is received in that bore and an end portion of reduced diameter at that end of that draw-bar. The end portion must be of diameter at least less than the outer diameter of the thread, otherwise it could not be screwed through the threaded bore. If the diameter of the end portion is between the inner and outer diameters of the thread, it must itself have at least partial threads formed on it. If the diameter of the end portion is less than the inner diameter of the thread it may be plain.
Providing screw-threaded portions at both ends of both draw-bars has the advantage that the integral heads are eliminated.
This improves the swept outline of the brake since no additional space is required to accommodate the heads.
The abutment members may comprise washers of generally "C" outline or split collets which are retained in position by means of cirelips.
In one construction the friction pad assemblies are guided to slide between spaced drag-taking abutment surfaces in the carrier member and the draw-bars extend through clearance openings in the carrier member, the actuating means being housed in one of the pressure plates against which the nuts abut, and the threaded portions at the ends of the draw-bars remote from the nuts being screwed into the bores which are provided in the other or reaction pressure plate which acts on the second friction pad assembly.
Two embodiments of our invention are illustrated in the accompanying drawings in which: Figure I is a section through one circumferential half of a disc brake; Figure 2 is an elevation of a portion of a pressure-plate into which a draw-bar is screwed; and Figure 3 is a view similer to Figure 2 but showing a modification.
The disc brake for vehicles illustrated in the accompanying drawings comprises a carrier member 1 of generally U-shaped outline which straddles the peripheral edge of a disc (not shown) and is mounted on a stationary part adjacent to one face of the disc.
Friction pad assemblies 2, 3 for engagement with opposite faces of the disc are guided for movement towards and away from the disc in the stationary member 1.
Each friction pad assembly 2, 3 comprises a pad 4 of friction material for engagement with the disc, and a rigid backing plate 5 carrying the pad 4 and having end edges slidably engaged with drag-taking abutment surfaces 6, 7 in the carrier member 1.
A clamping member 8 comprising a yoke assembly fitting over the disc comprises a pair of pressure plates in the form of an actuating beam 9 and a reaction beam 10 which are chordal with respect to the disc, and a pair of circumferentially spaced circular draw-bars of which only one is shown at 11 and which extend through clearance openings 12 in carrier member 1. The draw-bars 11 interconnect the pressure plates 9 and 10 at their outermost ends.
The actuator beam 9 is provided with a pair of hydraulic cylinders of which one is shown at 13, and an hydraulic piston 14 working in each cylinder acts on the friction pad assembly 2 to apply it directly to the disc when the cylinder 13 is pressurised through a passage 15. The reaction urges the actuating beam in the opposite direction in turn acting through the draw-bars 11 to apply the pad assembly 3 to the opposite face of the disc through the reaction beam 10.
The drag on the friction pad assemblies 2 and 3 when the brake is applied is taken by the surfaces 6, 7 and the clamp member 8 is located on the carrier member 1 on both sides of the disc in a known manner by pairs of booted pins 16 and 17.
In accordance with our invention each draw-bar 11 is provided at opposite ends with threaded portions 18 and 19, each terminating in an end portion 20, 21 of reduced diameter between which and the threaded portion 18, 19 is provided a radial groove 22, 23.
Each threaded portion 19 is screwed into an open-ended threaded bore 24 in the reaction beam 10, and the opposite end of each draw-bar projects through a clearance bore 25 in the actuating beam 9 to receive a nut 26 having an open-ended threaded bore 27.
A releasable coupling 28, 29 is provided between each end of the draw bar 11 and the nut 26 and the reaction beam 10 respectively. As illustrated each coupling comprises an abutment member comprising a washer 30, 31 of generally "C" outline which is of substantially the same thickness as the groove 22, 23 and which is received therein.
The washer 30, 31 is of an external diameter greater than that of the draw-bar 11 and is received in a groove in a counterbore 32, 33 in the outer end of the bore 27, 24 one face of the groove being defined by a shoulder at the step at the change in diameter, and the opposite face of the groove comprising a circlip 34, 35 releasably located in circlip grooves in the counterbore 32, 33. The washers 30, 31 can be released from the counterbore by removing the circlips 34, 35.
In assembling the brake each draw-bar 11 is first screwed through the bore 24 until the groove 23 projects from the reaction beam 10 by a distance sufficient to receive the washer 31. The draw-bar is then screwed in the opposite direction until the washer 31 engages with the stop face whereafter the circlip 35 is inserted to retain the washer 31 in position, determining a relative axial position for the draw-bar and locking the bar against rotation relative to the reaction beam 10.
The opposite end of each draw-bar is then inserted through the bores 12 and 25 and the nut 26 screwed onto the threaded portion 18 until the groove 22 projects from the nut 26 to receive the washer 30. Thereafter the nut 26 is screwed back in the opposite direction to clamp the washer 30 against the stop face whereafter the circlip 34 is inserted to retain the washer 30 in position, determining an axial position of the draw-bar with respect to the nut 26 and locking the draw-bar and the nut 26 against relative rotation.
The axial distance between the grooves 22 and 23 and the location of the stop faces in the reaction beam 10 and the nut 26 determines the effective or set length of the draw-bars 11.
An "0" ring 36 and a spring ring 37 retainer act between each draw-bar 11 and a counterbore 38 at the inner end of the clearance bore 25 to prevent rattle.
In the modified construction illustrated in Figure 3 each washer 30, 31 can be replaced by a two-part washer in the form of a split collet 39.
As described in the provisional specification No. 42013/76 accompanying the present application and divided from the provisional specification accompanying our co-pending British Patent Application No. 28776/76 (Serial No. 1567006) the circlips 34 and 35 may be axially resilient to compensate for variations in the tolerances of the grooves in which they are located and to avoid rattle.
For example, the circlips 34, 35 may be bowed, wavy or of conical outline.
In a modification, a resilient washer may be inserted between the circlip 34, 35 and the washer 30, 31. The purpose of providing resilience in the groove is that the tendency of the draw-bar to turn on its thread under heavy vibration is reduced. If the bar should turn, it would adopt a new axial position within the clearances permitted by the fit of the washers and circlip in the groove.
WHAT WE CLAIM IS: 1. A disc brake of the kind set forth for vehicles, in which each draw-bar is provided at at least one end with a screw-threaded portion, and a member in which that end of the draw-bar is connected has an openended screw-threaded bore into which the screw-threaded portion is screwed, a releasble coupling being provided between the said one end of each draw-bar and the member and at least one of said couplings comprising an abutment member releasably retained in a groove defined in the member and engaged within a groove in the draw-bar located between the screw-threaded portion and an end portion at the said one end of the draw-bar.
2. A disc brake according to claim 1, in which the end portion is of diameter less than that of the screw-threaded portion.
3. A disc brake according to claim 1 or 2, in which the member comprises one of the pressure plates.
4. A disc brake according to claim 1 or 2, in which the member comprises a nut screwed onto the end of the draw-bar which projects through a clearance bore in one of the pressure plates.
5. A disc brake according to claim 1 or 2, in which screw-threaded portions are provided at both ends of each draw-bar and one portion is screwed into an open-ended bore in one of the pressure plates and the other portion is passed through a clearance bore in the other pressure plate to receive a nut having an open-ended screw-threaded bore, releasable couplings being provided at both ends of each draw-bar, each coupling comprising an abutment member retained in a groove in one of the bores and engaged within a groove in the draw-bar located between the screw-threaded portion which is received in that bore and an end portion of reduced diameter at that end of that draw-bar.
6. A disc brake according to any of the preceding claims, in which the or each abutment member comprises a washer of generally "C" outline retained in position by means of a circlip.
7. A disc brake according to any of claims 1 to 5, in which the or each abutment member comprises a split collet retained in position by means of a circlip.
8. A disc brake according to claim 6 or claim 7, in which the or each circlip is axially resilient.
9. A disc brake according to claims 6, 7 or 8, in which a resilient washer is inserted between the abutment member and the circlip.
10. A disc brake according to any of
**WARNING** end of DESC field may overlap start of CLMS **.

Claims (12)

**WARNING** start of CLMS field may overlap end of DESC **. The washer 30, 31 is of an external diameter greater than that of the draw-bar 11 and is received in a groove in a counterbore 32, 33 in the outer end of the bore 27, 24 one face of the groove being defined by a shoulder at the step at the change in diameter, and the opposite face of the groove comprising a circlip 34, 35 releasably located in circlip grooves in the counterbore 32, 33. The washers 30, 31 can be released from the counterbore by removing the circlips 34, 35. In assembling the brake each draw-bar 11 is first screwed through the bore 24 until the groove 23 projects from the reaction beam 10 by a distance sufficient to receive the washer 31. The draw-bar is then screwed in the opposite direction until the washer 31 engages with the stop face whereafter the circlip 35 is inserted to retain the washer 31 in position, determining a relative axial position for the draw-bar and locking the bar against rotation relative to the reaction beam 10. The opposite end of each draw-bar is then inserted through the bores 12 and 25 and the nut 26 screwed onto the threaded portion 18 until the groove 22 projects from the nut 26 to receive the washer 30. Thereafter the nut 26 is screwed back in the opposite direction to clamp the washer 30 against the stop face whereafter the circlip 34 is inserted to retain the washer 30 in position, determining an axial position of the draw-bar with respect to the nut 26 and locking the draw-bar and the nut 26 against relative rotation. The axial distance between the grooves 22 and 23 and the location of the stop faces in the reaction beam 10 and the nut 26 determines the effective or set length of the draw-bars 11. An "0" ring 36 and a spring ring 37 retainer act between each draw-bar 11 and a counterbore 38 at the inner end of the clearance bore 25 to prevent rattle. In the modified construction illustrated in Figure 3 each washer 30, 31 can be replaced by a two-part washer in the form of a split collet 39. As described in the provisional specification No. 42013/76 accompanying the present application and divided from the provisional specification accompanying our co-pending British Patent Application No. 28776/76 (Serial No. 1567006) the circlips 34 and 35 may be axially resilient to compensate for variations in the tolerances of the grooves in which they are located and to avoid rattle. For example, the circlips 34, 35 may be bowed, wavy or of conical outline. In a modification, a resilient washer may be inserted between the circlip 34, 35 and the washer 30, 31. The purpose of providing resilience in the groove is that the tendency of the draw-bar to turn on its thread under heavy vibration is reduced. If the bar should turn, it would adopt a new axial position within the clearances permitted by the fit of the washers and circlip in the groove. WHAT WE CLAIM IS:
1. A disc brake of the kind set forth for vehicles, in which each draw-bar is provided at at least one end with a screw-threaded portion, and a member in which that end of the draw-bar is connected has an openended screw-threaded bore into which the screw-threaded portion is screwed, a releasble coupling being provided between the said one end of each draw-bar and the member and at least one of said couplings comprising an abutment member releasably retained in a groove defined in the member and engaged within a groove in the draw-bar located between the screw-threaded portion and an end portion at the said one end of the draw-bar.
2. A disc brake according to claim 1, in which the end portion is of diameter less than that of the screw-threaded portion.
3. A disc brake according to claim 1 or 2, in which the member comprises one of the pressure plates.
4. A disc brake according to claim 1 or 2, in which the member comprises a nut screwed onto the end of the draw-bar which projects through a clearance bore in one of the pressure plates.
5. A disc brake according to claim 1 or 2, in which screw-threaded portions are provided at both ends of each draw-bar and one portion is screwed into an open-ended bore in one of the pressure plates and the other portion is passed through a clearance bore in the other pressure plate to receive a nut having an open-ended screw-threaded bore, releasable couplings being provided at both ends of each draw-bar, each coupling comprising an abutment member retained in a groove in one of the bores and engaged within a groove in the draw-bar located between the screw-threaded portion which is received in that bore and an end portion of reduced diameter at that end of that draw-bar.
6. A disc brake according to any of the preceding claims, in which the or each abutment member comprises a washer of generally "C" outline retained in position by means of a circlip.
7. A disc brake according to any of claims 1 to 5, in which the or each abutment member comprises a split collet retained in position by means of a circlip.
8. A disc brake according to claim 6 or claim 7, in which the or each circlip is axially resilient.
9. A disc brake according to claims 6, 7 or 8, in which a resilient washer is inserted between the abutment member and the circlip.
10. A disc brake according to any of
claims 4-9, in which the friction pad assemblies are guided to slide between spaced drag-taking abutment surfaces in the carrier member and the draw-bars extend through clearance openings in the carrier member, the actuating means being housing in one of the pressure plates against which the nuts abut, and the threaded portions at the ends of the draw-bars remote from the nuts being screwed into the bores which are provided in the other or reaction pressure plate which acts on the second friction pad assembly.
11. A disc brake according to any preceding claim in which the or each screwthreaded bore is counterbored and a shoulder defined by the step at the change in diameter comprises one face of the groove in the member, the opposite face of the groove comprising a circlip located in a further groove in the counterbore and re leasable from its groove to allow the abut- ment member to be removed from the counterbore.
12. A disc brake substantially as herein described with reference to and as illustrated in the accompanying drawings.
GB4650075A 1975-11-11 1975-11-11 Disc brakes for vehicles Expired GB1567005A (en)

Priority Applications (9)

Application Number Priority Date Filing Date Title
GB4650075A GB1567005A (en) 1975-11-11 1975-11-11 Disc brakes for vehicles
US05/734,670 US4051925A (en) 1975-11-11 1976-10-21 Disc brakes for vehicles including a screw-threaded draw bar assembly
JP51134005A JPS5260380A (en) 1975-11-11 1976-11-08 Disc brake for wheel
FR7633607A FR2331715A1 (en) 1975-11-11 1976-11-08 DISC BRAKE IMPROVEMENTS FOR VEHICLES
SU762417312A SU689606A3 (en) 1975-11-11 1976-11-09 Disc brake for vehicle
BR7607518A BR7607518A (en) 1975-11-11 1976-11-10 DISC BRAKE IMPROVEMENT FOR A VEHICLE
IT7629183A IT1064154B (en) 1975-11-11 1976-11-10 IMPROVEMENTS TO DISC BRAKES FOR VEHICLES
DE19762651539 DE2651539A1 (en) 1975-11-11 1976-11-11 DISC BRAKE FOR VEHICLES
ES453201A ES453201A1 (en) 1975-11-11 1976-11-11 Disc brakes for vehicles including a screw-threaded draw bar assembly

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB4650075A GB1567005A (en) 1975-11-11 1975-11-11 Disc brakes for vehicles

Publications (1)

Publication Number Publication Date
GB1567005A true GB1567005A (en) 1980-05-08

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Family Applications (1)

Application Number Title Priority Date Filing Date
GB4650075A Expired GB1567005A (en) 1975-11-11 1975-11-11 Disc brakes for vehicles

Country Status (2)

Country Link
GB (1) GB1567005A (en)
SU (1) SU689606A3 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9744598B2 (en) 2001-07-26 2017-08-29 Ceramtec Gmbh Metal cutting tool and cutting plate provided in the shape of a donut

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9744598B2 (en) 2001-07-26 2017-08-29 Ceramtec Gmbh Metal cutting tool and cutting plate provided in the shape of a donut

Also Published As

Publication number Publication date
SU689606A3 (en) 1979-09-30

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