GB2102902A - Improvements relating to disc brakes - Google Patents
Improvements relating to disc brakes Download PDFInfo
- Publication number
- GB2102902A GB2102902A GB08222311A GB8222311A GB2102902A GB 2102902 A GB2102902 A GB 2102902A GB 08222311 A GB08222311 A GB 08222311A GB 8222311 A GB8222311 A GB 8222311A GB 2102902 A GB2102902 A GB 2102902A
- Authority
- GB
- United Kingdom
- Prior art keywords
- caliper
- taking member
- torque taking
- disc brake
- 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.)
- Granted
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
-
- 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
- F16D2055/0008—Brake supports
-
- 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
- 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
- F16D2055/002—Brake calipers assembled from a plurality of parts
-
- 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
-
- 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
- F16D2065/026—Braking members; Mounting thereof characterised by a particular outline shape of the braking member, e.g. footprint of friction lining
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
Abstract
The brake comprises a caliper (3) slidably mounted on a first torque taking member (1) by means of (a) pin sliding connection(s), the caliper (3) being open-topped for the insertion and removal of friction pad assemblies (27, 29). A supplementary torque taking member (5) is detachably secured to the first torque taking member (1) and has a pair of finger- like projections (15, 17) which, in use, engage in complementary recesses (19) in the friction pad assemblies (27, 29) and take all of the drag forces. To replace the pad assemblies (27, 29), the supplementary torque taking member (5) is detached (unbolted) to allow for easy access to the caliper (3). Various forms of pin sliding connections are disclosed. There may be a (third) sliding pin connection between the caliper (3) and supplementary torque taking member (5). <IMAGE>
Description
SPECIFICATION
Improvements relating to disc brakes
The present invention relates to a pin sliding caliper disc brake.
In particular the present invention relates to a sliding caliper disc brake for use in trucks, especially trucks in the medium range i.e.
4-12 tonnes GVW, vehicle manufacturers having a tendency towards adopting disc brakes instead of drum brakes, particularly in this medium range truck market. Disc brakes have advantages over drum brakes in terms of, for example, weight saving and stability. Further advantages are easier service ability and the ability to operate at higher temperatures than drum brakes without the "fade" problem which is inherent in drum brakes.
From the vehicle manufacturers point of view there are several features that individually or collectively are desirable when adopting a disc brake arrangement. These are as follows:- 1) For long pad life and thus longer service intervals, large volume friction pads may be required;
2) As large a disc as possible is required in order to minimise braking temperatures and as large a disc swept area to reduce input power per unit area;
3) An integral or ring mounted torque plate is preferred to allow for removal of the disc at major service intervals;
4) The brake is preferably of open top design to permit withdrawal of the friction pads radially with respect to the disc, without requiring removal of the caliper; and
5) Drag from the friction pad assemblies is required to be taken off directly by a fixed member e.g. torque plate.
A major disadvantage when thinking in terms of disc brakes for medium range trucks is the availability of space to actually install a caliper/torque plate, having all of the above features, coupled with the fact that the vehicle weight to wheel size relationship is comparable to that of heavier trucks and similar braking forces have to be met.
Certain known disc brakes for trucks, having what are termed fist or reaction type calipers, have had adequate friction pad volumes but pad changing has been a difficult operation. The caliper has had to either be swung out of the way or removed completely prior to removal of the friction pad assemblies and it can be appreciated that the calipers of such brakes are heavy and pad changing becomes a lengthy operation, see for example British Patent Specification No.
1526258, this being in comparison to smaller brakes of similar construction. This prior arrangement also provides for easier assembly and dismantling of the disc but rotation or removal of the caliper can result in the hydraulics being disturbed and the hydraulic hose can be twisted.
This is of course disadvantageous and possibly dangerous.
A further prior arrangement overcomes the above disadvantages by providing an open top caliper where a fixed member, i.e. torque plate, with circumferentially spaced limbs which span the disc are arranged to take both the pad drags.
Such a construction is shown in British Patent
Specification No. 2034425. However, this construction suffers from a reduced pad volume and area due to the pads having to be insertable through the open caliper top. Further, although the open top design clearly provides for easier pad change, the arrangement necessary to allow for the disc itself to be removed gives little abutment area for the outboard friction pad assembly, just where one would expect high wear at the pad/abutment interface.
Also in said fist type disc brakes, where the drag taking member straddles the disc and comprises circumferentially spaced limbs, the drag taking limb can deflect under high load. Such deflection can result in the spurious loading of the sliding connection between the caliper and torque taking member, causing binding etc.
It is known in certain fist type disc brakes to arrange the drag taking member above the disc periphery and centrally with respect to the pad.
Such a construction is shown in British Patent
Specification No. 1424976. However, there are certain disadvantages with this arrangement.
Firstly, at least part of the drag created by the outboard friction pad is taken through the caliper and thus the caliper/torque plate sliding pin connection must take some drag and this sliding connection could therefore distort and jam.
Secondly, although the drag taking member is centrally positioned with regard to the pads, it lies above the disc periphery and is thus spaced from the line of drag through the effective drag radius which is situated within the disc periphery. This can lead to an undue twisting moment being applied to the friction pad assemblies when the brake is activated, and jamming can result unless special provision is made to counter this moment.
The aim of the present invention is to try to overcome the above problems whilst providing a relatively inexpensive brake giving all of the advantageous features previously outlined as being desirable in a truck disc brake.
According to the present invention there is provided a pin sliding caliper disc brake, comprising a caliper and a first torque taking member, said caliper and first torque taking member being slidable relative to each other by means of a sliding pin connection, the caliper being open topped for the insertion of friction pad assemblies and a supplementary torque taking member being detachably secured to said first torque taking member, the supplementary torque taking member having a pair of projections which, in use, engage said friction pad assemblies and take all of the drag forces exerted on said friction pad assemblies.
Thus, by virtue of the present invention an open topped caliper design is achieved facilitating the easy replacement of friction pads and by virtue of the detachable supplementary torque taking member, the brake pads can be simply removed and the open top caliper can be designed without stress problems, to receive large volume/area friction pads. Also, and most importantly, the caliper is drag free, the torque taking member taking all of the drag forces. Thus the sliding pin connections between caliper and torque taking member, are free of drag preventing any distortion and jamming, as has occurred in prior art designs of the relevant type.
In a preferred embodiment of the present invention the supplementary torque taking
member has a pair of rectangular shaped fingers
which project generally radially of the brake disc
and engage in recesses in the backing plates of
the friction pad assemblies, the backing plates
having lateral shoulders which engage on support
guides in the caliper. Preferably, each friction pad
has a generally rectangular recess provided in the
middle region of the upper edge of the backing
plate, the recesses each being complementary in
shape to a rectangular finger of the supplementary
torque plate.The rectangular shaped fingers
which take all of the friction pad drag are
preferably so positioned as to extend into the
respective recesses to cover a point where all
elemental drag forces may be said to be combined
in a single drag force, this being below, i.e. within,
the brake disc periphery. Thus by virtue of the
location of the said recess in the middle region of
the upper edge of the backing plate, and the
rectangular shaped fingers covering the point
within the periphery of the brake disc, through
which all drag effectively acts, no undue twisting
moment is applied to the friction pad assemblies
when the brake is actuated.Further, the
supplementary torque taking member is preferably
bolted to the first torque taking member which is
preferably a ring torque plate, and thus by simply
unbolting the supplementary torque taking
member, easy pad replacement can be effected.
In truck disc brakes constructed according to
the present invention, which incorporate
mechanical or pneumatic actuators, where a
relatively large assembly is supported on the
caliper in contrast to a hydraulic arrangement, a
third pin sliding connection is preferably provided
between the caliper and the supplementary torque
taking member to thus maintain the caliper in a
stable position at all times as the friction pad
assemblies wear. Preferably the third pin engages
in the outboard finger projection of the
supplementary torque taking member.
All of the pin sliding connections in any
embodiment of the present invention are
preferably fully sealed, this being possible as the
torque plate and caliper need not be separate for
servicing.
The present invention will now be further
described, by way of example, with reference to the accompanying drawings, in which:
Fig. 1 is a front view of one embodiment of the present invention;
Fig. 2 is a partially cutaway plan view of the brake of Fig. 1;
Fig. 3 is a front view of the supplementary torque taking member of Figs. 1 and 2;
Fig. 4 is a plan view of the supplementary torque taking member of Figs. 1 and 2;
Fig. 5 is an end view of the supplementary torque taking member of Figs. 1 and 2;
Fig. 6 is an end elevational view of the brake of
Figs. 1 and 2;
Fig. 7 is a detailed plan view in cross section of part of the brake of Figs. 1 and 2, showing the sliding pin connection between torque plate and caliper;
Fig. 8 is a perspective view of a friction pad assembly for use in the brake of Figs. 1 to 7;;
Fig. 9 is a front view of a further embodiment of the present invention;
Fig. 10 is a partially cutaway plan view of the brake of Fig. 9;
Fig. 11 is a cross-sectional view of the brake of
Figs. 9 and 10;
Fig. 1 2 shows an alternative construction for the third pin of the brake of Figs. 9 and 10;
Fig. 1 3 shows one alternative embodiment of a fully sealed sliding pin connection between torque plate and caliper, suitable for the brake of the present invention; and
Fig. 14 shows a further alternative embodiment of a fully sealed sliding pin connection between torque plate and caliper, suitable for the brake of the present invention.
The disc brake constructed according to the present invention and illustrated in Figs. 1 to 7 of the accompanying drawings comprises a ring mounted torque plate 1, a caliper 3 and a supplementary torque taking member 5. The caliper 3 is mounted by slidable pin connections 7 and 9 on torque plate 1, and is basically of opentop design as can be seen at 11 in Fig. 2. When in use the open-top 11 is virtually completely covered, again as can be seen in Fig. 2, by the supplementary torque taking member 5 which is detachably secured to torque plate 1 by bolts 13.
As can be best seen in Figs. 3, 4 and 5, supplementary torque taking member 5 has a generally inverted U-shaped transverse crosssection configuration, with depending arms or finger-like projections 15 and 17. Each finger-like projection 15, 17 is received in a complementary recess 19, in the backing plate 23, 25 of a friction pad assembly 27, 29 (see Figs. 1, 2 and 7), the lateral edges 31 , 33 of each projection 15, 17 engaging the corresponding wall of a recess 19, so that the projections 1 5, 1 7 take all pad drag in either circumferential direction of movement. The friction pads can still slide relative to the projections 1 5, 1 7 axially of the disc as pad wear occurs (see Fig. 6), but are restrained by the projections in the circumferential direction with respect to the brake disc D. Thus all of the pad drag is conveyed to the torque plate 1 via the supplementary torque taking member 5 leaving the caliper 3 and the sliding pin connections 7 and 9, free of any drag forces obviating the possibility of any distortion due to drag forces, which distortion could lead to possible dangerous brake jamming. Each pin connection 7,9 is as shown in
Fig. 7 and comprises a pin 35 having a screw threaded portion 37 secured in a threaded bore 38 in caliper 3, and extension 39 of the pin 35 being slidably secured in a bore B in a sleeve 41 welded in position on torque plate 1. An annular flexible seal 43 seals the sliding pin connection.
Alternatively, reverse pin connections as, for example, shown in Figs. 13 and 14, can of course be equally well used.
It must also be noted that because the fingerlike projections 1 5, 1 7 project radially inwardly with respect to the brake disc they engage the friction pads at a theoretical point where all elemental drag forces can be said to be effectively combined in a single drag force i.e. within the disc periphery. This is clearly desirable and advantageous as it avoids or reduces undesirable moments of force.
To replace the friction pads 27, 29, the supplementary torque taking member 5 is unbolted from torque plate 1, disengaged from the friction pads 27, 29, and lifted clear of the brake.
The friction pads 27, 29 which merely rest with their lateral shoulders 45 on pad support guides 47 in caliper 3, can then be simply lifted out from the open-top caliper 3 and replaced, the supplementary torque taking member 5 being subsequently bolted back in position on the torque plate 1. Thus the caliper 3 remains in place though servicing on this truck brake can be simply carried out after removing the relatively light supplementary torque taking member 5.
Figs. 9, 1 0 and 11 of the accompanying drawings show a modified form of the disc brake of Figs. 1 to 8 and equivalent component parts to those shown in Figs. 1 to 7, are identified by the same reference numerals.
The main difference between the disc brake of Figs. 9, 10 and 11 and the brake of Figs. 1 to 8, are that the brake of Figs. 9, 10, 11 is a reverse pin slider, i.e. the sliding pins connecting the torque plate 1 and caliper 3, are secured to the torque plate 1, whereas the brake of Figs. 1 to 8 is a forward pin slide, and also the brake of Figs. 9, 10 and 11 is provided with a third sliding pin connection 48 are the outboard side of the brake to maintain the caliper steady, the caliper 3 being designed for mechanical or pneumatic actuation and therefore having to carry the heavy actuation assembly (not shown) not necessary on the hydraulic brake of Figs. 1 to 8.This third pin connection 48 therefore maintains the caliper 3 stable irrespective of pad wear and the position of the caliper 3 with respect to torque plate 1.
The construction of this third pin connection 48 is best seen in Fig. 11, the connection comprising a pin which is in the form of bolt 49, the shank 51 of bolt 49 passing through bore 53 in part of caliper 3 and being screwed into outboard fingerlike projection 1 7 of the supplementary torque taking member 5. Bore 53 is lined by bushing 55 which projects the sliding surface on shank 51. An alternative form of pin and seal for this third pin connection is shown in Fig. 12. In this alternative, the pin is merely a shaft 57, no bolt head being provided, the shaft 57 being screwed into the supplementary torque taking member 5. A bush 59 lines bore 53 but has flexible extensions which grip the shaft 57 beyond the bore 53 to thereby more effectively protect the sliding surface of the pin connection.
Figs. 13 and 14 merely show two reverse pin spider sliding connections for interconnecting the torque plate 1 and caliper 3, the sliding connections each comprising a pin 61 which is screwed into torque plate 1 and on which caliper 3 is slidable, the bore 63 in caliper 3 for receiving pin 61, being lined with a bush 65 in Fig. 12 and 67 in Fig. 13. Bush 65 (Fig. 13) has flexible extensions 69 and 71 which grip the pin surface beyond bore 63 and thereby offer complete protection for the sliding surfaces, whereas bush 67 (Fig. 14) is restricted to bore 63.
The above embodiments of the present invention provide a truck brake with virtually all of the required advantages initially listed, the major features being that the sliding caliper is free of drag and that, by virtue of the illustrated construction, the drag is taken at the theoretical point where all elemental drag forces effectively act as a single drag force.
Whilst the above embodiments of the present invention are of twin pin slider construction, the present invention is equally well applicable to any desired alternative construction of pin sliding disc brake.
Claims (12)
1. A pin sliding caliper disc brake, comprising a caliper and a first torque taking member, said caliper and first torque taking member being slidabie relative to each other by means of a sliding connection, the caliper being open-topped for the insertion of friction pad assemblies and a supplementary torque taking member being detachably secured to said first torque taking member, said supplementary torque taking member having a pair of projections which, in use, engage said friction pad assemblies and take all of the drag forces exerted on the friction pad assemblies.
2. A disc brake as claimed in claim 1, in which the supplementary torque taking member has a pair of projections in the form of shaped fingers which project generally radially of the brake disc, one on either side thereof, and engage in recesses in the friction pad assemblies.
3. A disc brake as claimed in claim 2, in which the friction pad assemblies each comprise a generally planar backing plate to which a pad of friction material is secured, each of said fingers engaging in a recess in the middle region of what is, in use, the upper edge of the backing plate.
4. A disc brake as claimed in claim 3, in which the fingers and recesses are complementarily shaped.
5. A disc brake as claimed in claim 4, in which the fingers and recesses are generally rectangular.
6. A disc brake as claimed in claim 3, 4 or 5, in which the backing plate has laterally projecting shoulders which engage guides in the caliper.
7. A disc brake as claimed in any one of claims 2 to 6, in which the fingers extend into the recesses in the friction pad assemblies, sufficiently for enough to cover a theoretical point within the periphery of the brake disc, through which the total pad drag effectively acts.
8. A disc brake as claimed in any one of the preceding claims, in which the first torque taking member is in the form of a ring shaped torque taking member, the suppimentary torque taking member being bolted thereto.
9. A disc brake as claimed in any one of the preceding claims, in which a third sliding pin connection is provided, this latter connection being between the caliper and the supplementary torque taking member.
10. A disc brake as claimed in claim 9, in which the third sliding pin connection is between the caliper and an outboard projection of the supplementary torque taking member.
11. A disc brake as claimed in any one of the preceding claims, in which each said sliding connection comprises a pin secured to the caliper and axially slidably received in a bore provided in said first torque taking member.
12. A disc brake as claimed in any one of claims 1 to 10, in which each said sliding connection comprises a pin secured to the said first torque taking member and axially slidably received in a bore provided in the caliper.
1 3. A pin sliding caliper disc brake, constructed substantially as hereinbefore described with reference to and as illustrated in the accompanying drawings.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB08222311A GB2102902B (en) | 1981-08-04 | 1982-08-03 | Improvements relating to disc brakes |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB8123757 | 1981-08-04 | ||
GB08222311A GB2102902B (en) | 1981-08-04 | 1982-08-03 | Improvements relating to disc brakes |
Publications (2)
Publication Number | Publication Date |
---|---|
GB2102902A true GB2102902A (en) | 1983-02-09 |
GB2102902B GB2102902B (en) | 1985-02-13 |
Family
ID=26280340
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
GB08222311A Expired GB2102902B (en) | 1981-08-04 | 1982-08-03 | Improvements relating to disc brakes |
Country Status (1)
Country | Link |
---|---|
GB (1) | GB2102902B (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0239282A1 (en) * | 1986-03-27 | 1987-09-30 | LUCAS INDUSTRIES public limited company | Disc brake for vehicles |
EP0665387A1 (en) * | 1994-02-01 | 1995-08-02 | BPW Bergische Achsen Kommanditgesellschaft | Disc brake |
US6962243B2 (en) * | 2002-10-07 | 2005-11-08 | Delphi Technologies, Inc. | Multi-disc brake system |
EP3779228A4 (en) * | 2018-03-27 | 2022-01-05 | Akebono Brake Industry Co., Ltd. | Floating-type disk brake |
-
1982
- 1982-08-03 GB GB08222311A patent/GB2102902B/en not_active Expired
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0239282A1 (en) * | 1986-03-27 | 1987-09-30 | LUCAS INDUSTRIES public limited company | Disc brake for vehicles |
EP0665387A1 (en) * | 1994-02-01 | 1995-08-02 | BPW Bergische Achsen Kommanditgesellschaft | Disc brake |
US6962243B2 (en) * | 2002-10-07 | 2005-11-08 | Delphi Technologies, Inc. | Multi-disc brake system |
EP3779228A4 (en) * | 2018-03-27 | 2022-01-05 | Akebono Brake Industry Co., Ltd. | Floating-type disk brake |
US11773931B2 (en) | 2018-03-27 | 2023-10-03 | Akebono Brake Industry Co., Ltd. | Floating-type disc brake |
Also Published As
Publication number | Publication date |
---|---|
GB2102902B (en) | 1985-02-13 |
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