AU687143B2 - A disc brake assembly - Google Patents

Description

WO 95/17612 PCT/AU94/00787 1 A DISC BRAKE ASSEMBLY The invention relates to disc brakes, and is particularly but not exclusively concerned with such brakes as used with motor vehicles. It will be convenient to hereinafter describe the invention by reference to motor vehicle wheel brakes, but it is to be understood that the invention has wider application.

In a typical disc brake assembly for a motor vehicle, a caliper bridge is arranged to straddle a rotatable disc. The bridge incorporates inboard and outboard portions each of which incorporates an associated friction pad. The portions are able to move relative to one another to enable the friction pads to engage opposing faces of the disc under the influence of a hydraulic piston cylinder assembly acting on the inboard portion.

In operation, stresses are induced in the brake assembly which cause deflection of the caliper. In one form of deflection, the caliper may stretch in an axial direction, i.e. in a direction parallel to the axis of rotation of the disc. In another form, the caliper may yawn or splay under load causing uneven loading to be applied to the disc by the pad assemblies. Furthermore, the caliper may tilt relative to the axis of the rotation of the disc causing the pads to tend to taper after continued use. These deflections are undesirable as they increase the fluid required to actuate the brakes, cause variations in the specific torque output of the brake assembly under different loadings, and result in uneven wearing of the pads.

To compensate for the effects of this loading, different caliper designs have been proposed to minimise the deflection of the caliper. However, these designs have not been completely effective in stopping deflection of the caliper.

Furthermore, these designs often add to the weight of the assembly, the complexity of its manufacture and the manufacturing costs. In addition these assemblies are often unable to dissipate heat as effectively due to the additional structure provided to make the brake assembly stiffer.

An aim of the present invention is to provide a disc brake assembly which is better able to accommodate the stresses induced in use of the brake assembly.

It is a further aim of the invention to provide a disc brake assembly which has WO 95/17612 PCT/A U94/00787 2 enhanced characteristics over prior art brake assemblies in relation to the cost of manufacture, its weight and its efficiency in dissipating heat.

In a first aspect, the present invention provides a disc brake assembly including, a disc having an axis of rotation and including a radially outer portion and a radially inner portion, a gap forming a radial separation between the said outer and inner portions and extending in a continuous circle ro-axial with said axis of rotation, two pad assemblies located on respective opposite sides of said disc and each being mounted for movement towards and away from said disc, and actuating means operable to cause each said pad assembly to move towards and engage the respective adjacent said side of the disc and including force transmitting means which extends through said gap and provides at least part of an interconnection between said pad assemblies such that one responds to movement of the other towards or away from said disc, wherein said actuating means includes a piston cylinder assembly in which the piston is movable relative to the cylinder along a movement axis, either the cylinder or the piston being connected to said other pad assembly for movement therewith, and said force transmitting means including a draw bar extending co-axial with said movement axis and connecting either said piston or said cylinder respectively to said one pad assembly.

Preferably each pad assembly overlies part of each of the outer and inner disc portions and is engagable with the outer and inner portions on respective sides of the disc.

By locating the force transmitting means to extend through the gap in the disc, a caliper bridge is no longer required. Furthermore when each pad assembly is engagable with both the outer and inner disc portions, the brake assembly is better able to accommodate the loads induced in operation of the assembly as the bending moment on the force transmitting means generated by the contact surface which is at a radially outer side of the force transmitting means is offset by the bending moment generated by the contact surface at the radially inner side. Furthermore, with the draw bar extending along the axis of movement of the piston relative to the cylinder, bending stresses acting on the force transmitting means are minimised and the clamping load in the brake assembly is able to be transferred substantially along the force transmitting means. Consequently, the bending moment in the force transmitting means is reduced or even eliminated as compared to a conventional caliper bridge.

The individual pad assemblies include a section of friction material, with a surface of the friction material forming an operative surface of the respective pad assembly. Each pad assembly may incorporate separate sections of friction material, each of which has a discrete operative surface. However, for the purposes of this specification, the discrete operative surfaces of a respective pad assembly shall be collectively referred to as "an operative surface" for that pad assembly and may be considered as a single entity which has an outer perimeter defined by outer edges of the discrete operative surfaces.

Preferably the one pad assembly is pivotally retained or rigidly secured to the force transmitting means whereas the other pad assembly is slidably mounted to the force transmitting means for movement away or towards the one pad assembly. Preferably the cylinder or piston is connected to the other pad assembly.

Preferably, the brake assembly incorporates an anchor bracket which is securable to a support structure and includes a body on which one of the pad 0 assemblies is mounted to accommodate torque forces generated in use of the *i 20 assembly. Preferably the bracket includes a pair of support elements which extend through the gap and are connected to the other pad assembly to at least assist in guiding movement of that pad assembly.

In a further aspect, the present invention relates to a brake sub assembly for use on a disc brake assembly incorporating a disc, the brake sub assembly 25 including two pad assemblies separated by a space and being locatable on respective opposite sides of said disc, and actuating means operable to cause relative movement of the pad assemblies to vary said space and including force transmitting means providing at least part of an interconnection between said pad S"assemblies such that one responds to movement of the other, wherein said actuating means includes a piston cylinder assembly in which the piston is movable relative to the cylinder along a movement axis, either the cylinder or piston being connected to said other pad assembly for movement therewith and 4 EA\DJH \13079sp said force transmitting means including a draw bar extending co-axial with said movement axis and connecting either said piston or said cylinder respectively to said one pad assembly.

Each pad assembly includes an operative surface and the force transmitting means is operable to apply a force to one of the pad assemblies at a location substantially coincident with a central region of the operative surface of that pad assembly. An advantage of invention is that as the draw bar extends co-axial with the piston cylinder assembly, the draw bar can be connected to the other pad assembly at a position which provides a preferred load distribution on the support member of that pad assembly. In this way, deflection of the pad assembly in operation of the assembly may be minimised.

Preferably the brake pad assembly includes a support member and a friction lining connected to, or integrally formed with, the support member, a surface of the friction lining forming an operative surface of the pad assembly having relative to the axis of rotation, a radially outer and a radially inner edge interconnected by two side edges, the pad assembly incorporating at least one passage extending through said friction lining and at least into the support member, the or each passage being arranged for receiving a force transmitting element operable to interconnect the pad assembly with another pad assembly, 20 and abutment surfaces located on opposite sides of said support member, the o abutment surfaces being engagable with respective support elements of the disc brake assembly and being adapted to transfer torque loading from said brake pad assembly to said support member on operation of said disc brake assembly.

Preferably a region of the operative surface corresponds to the or each 25 passage, each region being approximately a size proportional to an expected actuation load induced on the operative surface by the force transmitting element received within the respective passage and wherein, the or each passage is located substantially at the centre of that region.

S"Further the passage may extend to an edge of the pad to thereby facilitate lateral release of the pad from the force transmitting element.

The friction lining may also be separated into two parts by a space which extends transverse to the rotational axis of the disc with each part of the friction E.\DJHA3079sp lining being engagable with a respective one of two radially separated portions of the disc.

Preferably a disc of the disc brake assembly includes braking surfaces on each of the two opposite sides of the inner and outer portions and connecting means spaced from the braking surfaces and interconnecting the inner and outer portions of the disc, the connecting means being in the form of a bracket located on one side of the disc, the bracket being spaced from the braking surface on that side of the disc to form a cavity in which a brake pad assembly is able to be located, the bracket further incorporating at least one passage providing access to the cavity.

Preferably the braking surfaces are provided on both the inner and outer portion and when used with a brake pad assembly as described above, the respective braking surfaces provide suitable engagement surfaces for the operative surfaces of the respective brake pad assemblies. Furthermore, the force transmitting means and the anchoring bracket are able to pass through the aperture in the disc, without inhibiting rotation of the disc.

Preferably there are a plurality of passages formed in the bracket. This arrangement also assists in ventilation of the assembly.

It will be convenient to hereafter describe various embodiments of the V 0** 20 invention in greater detail with reference to the accompanying drawings. The 0000 *0 00 0 *oo 0 0000 0.

E DJH\13079sp WO 95/17612 PCT/AU94/00787 6 particularity of these drawings in the related description is not to be understood as superseding the generality of the preceding broad description of the invention.

In the drawings: Figure 1 is an exploded perspective view of a sub assembly for a disc brake assembly according to a first embodiment of the invention; Figure 2 illustrates a variation of the sub assembly of Figure 1; Figure 3 is a sectional view of the first embodiment of a disc for use in a disc brake assembly according to the invention; Figure 4 is a sectional view of a second embodiment of a disc for use in the disc brake assembly according to the invention; Figure 5 is a variation of the disc of Figure 4; Figure 6 is a perspective view of a disc brake assembly including the sub assembly of Figure 1; Figure 7 is a sectional view along section line VII-VII of Figure 6 and illustrating a full cast disc; Figure 8 is a perspective view of a variation of the brake pad assembly for use in the sub assembly of Figure 1; Figure 9 illustrates a machining tool for preparation of the braking surfaces of the disc of the disc brake assembly; Figure 10 is a variation of the machining tool of Figure 9 incorporating two cutting heads; and Figure 11 is a schematic view of the braking surfaces on a disc using the machining tools of either Figure 9 or Figure 1 illustrates a sub assembly 10 of a disc brake assembly 100 according to an embodiment of the invention. This figure is an exploded view to more clearly disclose the various component parts.

The sub assembly incorporates inboard and outboard friction pad assemblies (11 and 12 respectively), each of which incorporates a support plate (13, 14) and a friction pad (15, 16). Typically, each friction pad is bonded or riveted to its respective support plate to transmit shear load.

An anchor bracket 17 is adapted to be mounted to a motor vehicle through mounting holes 18. Guide rails 19 extend along opposing sides of the bracket to WO 95/17612 PCITAU94/00787 7 support the inboard and outboard assemblies. Cooperable slots 20 are located on the respective inboard and outboard assemblies 11, 12 and receive the guide rails enabling the assemblies to be slidably mounted on the anchor 17 in a direction away or towards each other. It should be appreciated that the pad assemblies may be secured to the anchor bracket 17 in other ways, such as with slideways located on the anchor bracket arranged to receive respective ends of the assemblies, or by a pin guided arrangement.

Two cylinder piston assemblies (22, 23) form the actuating means 21 of the sub assembly 10. Each cylinder piston assembly includes a cylinder 24 mounted to the inboard pad assembly through bracket 25, and piston 26. In each cylinder piston assembly, the piston 26 is slideable within the cylinder 24 along a movement axis 71 (Figure 7) and movable in a direction away or towards the support plate 13 of the inboard assembly 11 under hydraulic pressure. A seal 27 (Figure 7) is located between the piston 26 and cylinder 24 and a boot (not shown) is located on the cylinder on the inboard side of the seal 27. It should be realised a single cylinder could be used and that the number of cylinders in the assembly 10 may vary depending on the size of the assembly as well as the specific torque output required. Furthermore, the cylinders may be secured to the support plate 13 in any suitable form including integrally forming the cylinders with the support plate. Furthermore, it may be desirable to have only a reduced contact area between the cylinder and the plate and this arrangement is illustrated in Figure 7.

Force transmitting means 28 in associated with the actuating means 21 to provide at least part of an interconnection between the pad assemblies such that the inboard assembly responds to movement of the outboard assembly towards or away from the disc. In the first embodiment, the force transmitting means 28 is in the form of rods 29 associated with each cylinder piston assembly and which extend coaxial with the movement axis. In Figure 1 the rods are integrally formed with respective piston 26. In an alternative arrangement (not shown) each piston is connected to the rod through any appropriate coupling means such as a screw thread arrangement. Rods 29 pass through apertures (30, 31, 32) in the respective cylinders 24 and pad assemblies 11 and 12 and are secured to the WO 95/17612 PC'iAU94/00787 8 outboard support plate 14. The rods 29 are slideable within the apertures 30 and 31 enabling the rods to be movable relative to the cylinders 24 and the inboard pad assembly 11. A seal 33 (Figure 7) is provided in the respective apertures to seal between the respective rods 29 and the cylinders 24.

While the rods 29 may be secured to the support plate 14 in any suitable way, in the illustrated arrangement of Figure 1, each rod incorporates a threaded stud 34 on its outer end which is arranged to receive a cooperable nut Furthermore, the rod 29 is keyed to the support plate 14 to prevent relative rotation thereof during tightening of the nut 35 by a portion 36 located adjacent the stud 34 and having a rectangular or any other non-circular shape crosssection which is received in the suitably shaped aperture 32 in the outboard support plate. Furthermore, the rods 29 are positioned across the support plate 14 at a position to optimise the load distribution induced on the plate 14 by the rods 29. In this arrangement, as there are two rods, the friction pad 16 may be divided notionally into two regions with each rod connected at a centre of a respective one of the regions. To evenly distribute the load across the plate the size of each region would be proportional to the expected actuation load induced by each rod. In the illustrated case as each rod is expected to transmit half the actuation load, the size of these regions is approximately the same.

In an alternative arrangement shown in Figure 2, each rod 29 incorporates an enlarged T-shaped head portion 37 and each aperture (31, 32) in the pad assemblies is elongated to accommodate entry of the respective head portions.

The rods 29 are arranged to be secured to the outboard support plate 14, once the respective heads have passed through apertures 32, by rotating the rods through 900 The heads are biased towards support plate 14 to minimise rattle by some form of spring clip (not shown). At the same time this clip also acts as an antirotational device for the head. In this arrangement, the rods are typically connected to the pistons via screw threads (not shown).

The friction pad (15, 16) of each pad assembly (11, 12) provides a operative surface (38, 39) which in use is arranged to engage respective sides of a disc (Figure While the friction pad may be unitary, in the illustrated arrangement, the operative surface of the respective pad assemblies incorporates channels WO 95/17612 PCT/AU94/00787 9 and 41 which divide each operative surface into four discrete parts. One channel extends longitudinally across each pad assembly and incorporates the respective apertures (31, 32) to receive respective rods 29. The other channel 41 extends substantially transverse to this channel 40. Other arrangements of channels may be provided if required.

As illustrated in Figure 8, a quick release pad assembly 42 is provided comprising a support plate 43 and friction pad 44. Apertures 45 are formed through the plate and pad which are arranged to receive respective rods 29.

Each aperture is in the form of a radial slot which extends preferably from the radially lower edge 46 of the pad assembly 42 to enable quick release of the pad assembly from the brake sub assembly.

Figure 3 illustrates a first embodiment of the disc 50 which may be used in association with the sub assembly 10 to form the disc brake assembly 100.

The disc 50 is arranged to rotate about an axis of rotation 51 and rotate with the motor vehicle. The disc has an inboard side 52 and an outboard side 53 and incorporates a radially inner portion 54 and a radially outer portion 55 which are separated by gap 56 extending in a continuous circle coaxial with the axis 51 of the disc.

Each portion (54, 55) has a respective inboard and outboard braking surface (57, 58, 59, 60) located on opposite sides of the disc 50. These braking surfaces provide the engagement surfaces for the operative surfaces (38, 39) of the respective pad assemblies.

A bracket 61 is located on the outboard side of the disc 50 and interconnects the inner and outer portions (54, 55). The bracket 61 is secured to the inner and outer portions and is spaced from the inner and outer portion outboard braking surfaces (58, 60) to provide a cavity 62 in which the outboard assembly 12 is located, enabling the operative surface 39 of the outboard assembly to engage the outboard braking surface (58, 60) of the inner and outer portions.

A second embodiment of the disc 50 is illustrated in Figure 4. This disc is similar to the disc of Figure 3 and incorporates the radially inner and outer portions (54, 55) separated by the gap 56. However in this arrangement, the disc forms part of the wheel assembly 63. The wheel assembly includes a hub 64, a WO 95/17612 I'C'17AU94/00787 rim 65, and a plurality of spokes 66 interconnecting the hub and rim. In Figure 4, the inner and outer portions are bolted, or otherwise rigidly connected, to the wheel assembly 63. This arrangement is feasible for use where the wheel incurs little side loading (eg. in cornering) and therefore, is not subjected to bending of the rim relative to the hub. An example of such a situation would be with a motor cycle.

A variation of this disc 50 is illustrated in Figure 5 which may be used in motor vehicles where cornering loads could deflect the rim relative to the hub. In this case, the inner portion 54 is fixed to the hub 64 and the outer portion is attached to the rim 65 or spoke 66 in a manner that allows limited movement in the axial direction such as through a spline 67 as illustrated, or through key/keyways or drives. In alternative arrangements (not shown), to maintain correct alignment of the inner and outer portions, the inner portion is movable relative to the hub in an axial direction, while the outer portion is fixed, or both the inner and outer portions are movable in the axial direction with the sub assembly being fixed to form a datum surface. A further embodiment of the disc is illustrated in Figure 7 which comprises a fully cast disc 50. This disc is arranged to be connected solely to the hub and therefore deflection of the rim relative to the hub does not cause misalignment of the inner portion relative to the outer portion.

Figures 6 and 7 illustrate the disc brake assembly 100 incorporating the sub assembly 10 and disc 50. The inboard and outboard pad assemblies (11, 12) are supported on the anchor bracket 17 and are located on opposing sides of the disc with the guide rails 19 of the bracket 17 extending through the gap 56. The outboard pad assembly 12 is located in the cavity 62. The disc 50 includes a series of passages 68 which are formed in the bracket 61 to provide access to the cavity 62 and also improve ventilation around the disc. The cylinders 24 are connected to the inboard assembly 11 and the rods 29 are connected to the respective pistons 26 and extend through the gap 56 and are connected to the outboard pad assembly 12. The movement axis 71 of each piston relative the respective cylinder is substantially parallel to the axis of rotation 51 of the disc and each piston 26 is arranged to move away from the inboard assembly in operation of the brake along the movement axis 71 with the rods 29 acting as a WO 95/17612 i'1C'(A1U94/0(787 11 draw bar which draws the outboard assembly towards the inboard assembly causing the operative surface 39 to be drawn into engagement with the outboard braking surface (58, 60) of the disc 50. As the inboard assembly 11 is movable on the anchor bracket 17, on continued movement of the pistons 26 away from the inboard assembly 11, the inboard pad assembly is cau,.ao to move on the guide rails 19 on the bracket 17 to move the operative surface 38 of the inboard assembly 11 into engagement with the inboard face (57, 59) of the disc An advantage of the disc brake assembly 100 is that each rod 29 is much better able to accommodate the loads induced in operation of the assembly than prior art caliper bridge arrangements by virtue of the location of each rod relative to the operative surfaces and to the axis of movement of the respective pistons.

In this arrangement, the loads induced at these operative surfaces are transferred substantially along each rod with little bending moment being applied with any drag load or torque induced at the respective pad assemblies being transferred to the anchor bracket through their point of contact on the guide rails 19. As a result, the brake assembly provides a much stiffer arrangement with deflection of the brake assembly due to operational loading being substantially reduced. As a result, the operative surface of the pad assemblies on the disc will not change under increased loading thus enabling the brake assembly to give a more consistent specific torque output under different loadings. Furthermore, with the stiffer construction, the pad assemblies may include larger surfaces and the piston cylinder arrangement is more efficient requiring a lower fluid displacement.

To inhibit binding of the piston within the cylinder without compromising the efficiency of the assembly, a portion 70 of the cylinder wall between seals 33 and 27 is relieved. In this way, the possibility of binding of the piston 26 can be reduced without compromising the effectiveness of the sealing arrangement between the piston 26 of the cylinder 24 or rod 29. A neat fit is provided between the cylinder and the piston or rod on either side of respective seals 33, 27. This ensures that extrusion of the seals does not occur which would otherwise increase fluid displacement. While the rod 29 takes very little bending movement, any side loading on the rod reacts against cylinder 27 at the location adjacent the seals 27, 33 which provide a bearing surface for the piston or rod.

WO 95/17612 PCT/AU94/00787 12 Furthermore, as each rod is more efficient in accommodating the stresses induced in the assembly, and as a caliper bridge is no longer required, the brake assembly can be of lighter construction and manufacturing costs can be reduced.

Furthermore, as it is not required to provide space for a caliper bridge on the radial extremity of the disc, a larger diameter disc is possible which provides a larger heat sink for the brake assembly, and a larger effective radius.

In addition the brake assembly 10 is well equipped to effectively dissipate heat in operation of the assembly. In relation to the disc, with the radial separation there is more surface area in the disc and vents 69 formed between the braking surface are shorter. Furthermore, the longitudinal channel 40 in each pad assembly is arranged to be located over the gap 56, providing a gap which allows air flow around the contact surfaces. The transverse channels 41 further assist in encouraging the air flow. Furthermore, with this arrangement, there is no caliper bridge or other struzture to shield heat dissipation.

A further advantage is that the brake assembly may be more easily removed from the disc. As a caliper bridge is not required, once the rods are disconnected from the outboard pad assembly, the brake assembly may be withdrawn from the disc by being moved in the axial direction. Furthermore, the pad assemblies may be changed without removal of the wheel. For example, in the brake assembly shown in Figure 2, the rods are released from the outboard pad assembly by being rotated through 900, and this can be effected from the outboard side of the disc through passages 68. The inboard pad assembly and piston cylinder arrangement is then withdrawn from the disc in the axial direction and the outboard pad assembly is removed through the spokes in the wheel provided an adequate gap exists between adjacent spokes. A similar operation can be undertaken to install the new pad assemblies.

Further benefits can be realised in the disc brake assembly 100 by the design and method of manufacture of the disc The disc 50 may be formed in one piece or may be cast in separate pieces and assembled later. In one embodiment, the bracket 61 forms part of a centre support 76 which is secured to an axle for rotation with the vehicle. Typically the centre support is made from steel and is fabricated or pressed or formed from a WO 95/17612 1CPI'AU94/00787 13 combination thereof. The inner and outer portions (54, 55) of the disc are cast or otherwise formed on to the bracket. Each portion may be formed as a single piece or may be formed from a plurality of interfitting segments These portions may be cast from any suitable material including aluminium, metal matrix composition or cast iron. Alternatively, the bracket and inner and outer portions may be cast from a single material and integrally formed together as shown in Figure 7.

To prepare the necessary inboard and outboard braking surfaces (57, 58, 59, the portions may be machined using a chip producing process including grinding, turning and milling. The surfaces usually need to be planar and have a suitable surface texture to expedite burnishing of the friction pads.

Figure 9 illustrates a suitable machining tool located in the disc 50 to provide the outboard braking surfaces (58, 60). The machining tool 77 incorporates a head 78 mounted on a rotatable shaft 79. Cutters 80 (which may include single point or multiple point cutting edges) are secured to the head and are spaced from the axis of rotation 81 of the shaft and are separated by an angle which is approximately 180. The spacing determines the depth of the respective braking surface of the inner and outer portions.

To prepare the outboard braking surface, the tool is inserted in through the gap 56 within the disc 50. To facilitate insertion of the head 78 in through the gap 56, the machining tool 77 is of suitable shape, such as substantially T-shape as illustrated with the cross piece being arcuate to enable insertion into the gap 56 or in an alternative embodiment (not shown), of a substantially L-shaped configuration. To machine the face, the cutters 80 are located against the disc surface and the tool 77 rotates about the shaft causing the cutters to move against the disc surface. To vary the depth of the cut, relative axial movement between the tool and the disc is provided. The disc 50 is also caused to rotate to provide feed for the tool 77.

The relative speed of the rotation of the disc compared to the tool 77 determines the finish on the surface. If the disc rotates more slowly than the tool, a milling process occurs at the surface. If the disc rotates at a faster speed than the tool, then a process similar to a turning process occurs though the rake angle WO 95/17612 PCT/AU94/100787 14 of the cutter would not remain constant as in an ideal turning process due to the rotation of the cutter shaft.

The milling process is preferred because the resultant finished texture is of a cris-cross pattern 84 (which is illustrated in Figure 11) which is believed to be better for burnishing the surface than the pattern produced by a turning process, which is similar to a spiral.

To prepare the inboard braking surface, a similar tool (not shown) is used except the cutters face outboard rather than inboard as in the tool 77. The inboard surface may be prepared separately or simultaneously with the preparation of the outboard surface. In the latter arrangement, the two machining tools would typically be spaced circumferentially about the disc.

An alternative tool 82 is illustrated in Figure 10. This tool is substantially the same as the tool illustrated in Figure 9 except that an additional head 83 is incorporated on a concentric shaft 85 in a position spaced from the head 78. In this arrangement, cutters are located on opposing faces of the heads 78 and 83 and as in the earlier embodiment, the cutters on each head are radially spaced from the axis of rotation of the shaft and separated by an angle which is approximately 1800, though other angles may be used. For example the angle may be 900 which may assist in minimising vibration. The concentric shaft 85 is provided to enable axial displacement between each head and the disc to enable the depth of cut to be varied.

With the tool 82 the inboard and outboard braking surfaces can be processed simultaneously thereby enabling the processing time to be further reduced. In other respects the tool 82 processes the faces on the disc in the same way as the earlier embodiment. In yet another alternative, two heads are provided spaced along the axis of the shaft with each head only having a single cutter which is arranged to cut a respective one of the opposing inboard and outboard faces. In this arrangement, each cutter is radially spaced from the axis of rotation of the shaft with the angle between the cutters about the axis of rotation being typically zero such that the cutters are arranged to straddle a particular portion of the disc, or at approximately 1800 such that one cutter is arranged to engage the inner WO 95/17012 PCT/A U94/00787 portion of the disc while the other cutter engages the outer portion or at any other relative angular position.

In an alternative arrangement (not shown) the first portion of the disc may be formed separately from the second portion and may be processed individually, or assembled, and then processed simultaneously. Each of these pieces may be formed in one uniform material or may be composite or incorporate inserted portions.

In the manufacture of the disc either as a single piece or in separate pieces, each portion may be solid or ventilated or the disc may be formed with one portion ventilated and the other solid depending on the performance characteristics required.

It will be appreciated from the foregoing description that the disc brake assembly, sub assembly and disc in accordance with the invention provides an arrangement which is better abie to accommodate the loads involved in operation of the brake assembly while being of light weight construction, being relatively inexpensive and effective in dissipating heat.

Finally it is to be understood that various alterations, modifications and/or additions may be introduced into the construction and arrangements previously described without departing from the spirit or ambit of the invention described.

Claims (30)

1. A disc brake assembly including, a disc having an axis of rotation and including a radially outer portion and a radially inner portion, a gap forming a radial separation between the said outer and inner portions and extending in a continuous circle co-axial with said axis of rotation, two pad assemblies located on respective opposite sides of said disc and each being mounted for movement towards and away from said disc, and actuating means operable to cause each said pad assembly to move towards and engage the respective adjacent said side of the disc and including force transmitting means which extends through said gap and provides at least part of an interconnection between said pad assemblies such that one responds to movement of the other towards or away from said disc, wherein said actuating means includes a piston cylinder assembly in which the piston is movable relative to the cylinder along a movement axis, either the cylinder or the piston being connected to said other pad assembly for movement therewith, and said force transmitting means including a draw bar extending co-axial with said movement axis and connecting either said piston or said cylinder respectively to said one pad assembly.

2. A disc brake assembly according to claim 1, wherein each said pad assembly overlies part of each of said outer and inner disc portions and is engagable with the respective said adjacent side of- the disc at both said outer and inner portions.

3. A disc brake assembly according to either claim 1 or 2, wherein the draw bar extends through an aperture in the other of said cylinder or piston to which it is connected, and wherein a first seal is provided in said aperture to provide a sealing engagement therebetween.

4. A disc brake assembly according to claim 3, wherein a second seal is provided between said piston and cylinder to provide sealing engagement therebetween.

5. A disc brake assembly according to claim 4, wherein a part of the cylinder wall intermediate the first and second seals is relieved to provide a clearance between said piston and said cylinder. LI, AMENDED SHEED a a.. a.. a a a a a

6. A disc brake assembly according to any preceding claim, wherein the draw bar extends through an aperture provided in at least said other pad assembly.

7. A disc brake assembly according to any preceding claim, wherein each said pad assembly includes a section of friction material, and a surface of said friction material forms an operative surface of the respective pad assembly which is engagable with said disc.

8. A disc brake assembly according to claim 7, wherein said force transmitting means is operable to apply a force to said one pad assembly at a location substantially coincident with a central region of said operative surface of that pad assembly.

9. A disc brake assembly according to any preceding claim, wherein the actuation means includes a plurality of said piston cylinder assemblies each incorporating a respective said draw bar.

10. A disc brake assembly according to any preceding claim, further including an anchor bracket securable to a support structure, the anchor bracket including a pair of support elements arranged to extend through said gap to support said pad assemblies and accommodate torque loading induced in operation of the assembly.

11. A brake sub assembly for use on a disc brake assembly incorporating a disc, the brake sub assembly including two pad assemblies separated by a space and being locatable on respective opposite sides of said disc, and actuating means operable to cause relative movement of the pad assemblies to vary said space and including force transmitting means providing at least part of an 25 interconnection between said pad assemblies such that one responds to movement of the other, wherein said actuating means includes a piston cylinder assembly in which the piston is movable relative to the cylinder along a movement axis, either the cylinder or piston being connected to said other pad assembly for movement therewith and said force transmitting means including a draw bar extending co-axial with said movement axis and connecting either said piston or said cylinder respectively to said one pad assembly.

12. A brake sub assembly according to claim 11, wherein the draw bar extends through an aperture in the other of said cylinder or piston to which it is connected S E:\DJH \13079sp 4 A 18 and wherein a first seal is provided in said aperture to provide a sealing engagement therebetween.

13. A disc brake sub assembly according to claim 12 wherein a second seal is provided between said piston and cylinder to provide sealing engagement therebetween.

14. A disc brake sub assembly according to claim 13 wherein a part of the cylinder intermediate the first and second seals is relieved to provide a clearance between said piston and said cylinder. A brake sub assembly according to either claim 11 to 14, wherein the draw bar extends through an aperture provided in at least said other pad assembly.

16. A brake sub assembly according to any one of claims 11 to 15, wherein each said pad assembly includes a section of friction material, and a surface of said friction materials forms an operative surface of the respective pad assembly which is engagable with said disc.

17. A brake sub assembly according to claim 16, wherein said force transmitting means is operable to apply for a force to said one pad assembly at a location substantially coincident with a central region of said operative surface of that pad assembly.

18. A brake sub assembly according to any one of claims 11 to 17, wherein the actuation means includes a plurality of said piston cylinder assemblies each :.,'incorporating a respective said draw bar. A brake sub assembly according to any one of claims 11 to 15, further including an anchor bracket securable to a support structure, the anchor bracket including a pair of support elements arranged to support said pad assemblies and 25 accommodate torque loading induced in operation of the assembly. A disc brake assembly according to claim 10 wherein each pad assembly S6 includes a support member and a friction lining connected to, or integrally formed with, the support member, a surface of the friction lining forming an operative surface of the pad assembly having relative to the axis of rotation, a radially outer and a radially inner edge interconnected by two side edges, each pad assembly incorporating at least one passage extending through said friction lining and at least into the support member, the or each passage being arranged for receiving S EA\DJH\A13079sp 19 the drawbar interconnecting the pad assemblies, and abutment surfaces located on opposite sides of said support member, the abutment surfaces being engagable with the respective support elements of the anchor bracket and being adapted to transfer torque loading from said brake pad assembly to said support elements on operation of said disc brake assembly.

21. A disc brake assembly according to claim 20, wherein a region of the operative surface corresponds to the or each passage, each region being approximately a size proportional to an expected actuation load induced on the operative surface by the force transmitting element received within the respective passage and wherein each passage is located substantially at the centre of that region.

22. A disc brake assembly according to either claim 20 or 21, wherein the abutment surfaces are located in recesses formed in the said opposite sides of said support member, the recesses being adapted to receive the support elements of the disc brake assembly therein.

23. A disc brake assembly according to any one of claims 20 to 22, wherein the or each passage extends to a radially inner edge of the support member.

24. A disc brake assembly according to any preceding claim wherein the disc further includes a braking surface on each of the two opposite sides of the outer 20 and inner portions, and connecting means spaced from the braking surfaces and interconnecting the inner and outer portions of the disc, the connecting means being in the form of a bracket located on one side of the disc, the bracket being spaced from the braking surface on that side of the disc to form a cavity in which a brake pad assembly is able to be located, the bracket further incorporating at 25 least one passage providing access to the cavity.

25. A disc brake assembly according to claim 24, wherein the bracket includes a plurality of passages.

26. A disc brake assembly according to either claim 24 or 25, wherein the bracket is adapted to be connected to a hub of a wheel assembly so as to connect the disc to said wheel assembly.

27. A disc brake assembly according to any one of claims 24 to 26, wherein at least one of the outer or inner portion is movable relative to the other of the outer EA\DJH\13079sp or inner portion in a direction substantially parallel to the axis of rotation of the disc.

28. A disc brake assembly according to any one of claims 24 to 27, wherein at least one of the inner or outer portions is formed from a plurality of segments.

29. A disc brake assembly according to any one of claims 24 to 28, wherein the inner and outer portions and the bracket is formed as a single piece. A disc brake assembly according to any one of claims 24 to 28, wherein the inner and outer portions are connected to the bracket.

31. A disc brake assembly according to any one of claims 24 to 30, wherein the inner and outer portions are formed from different materials.

32. A disc brake assembly according to any one of claims 24 to 31, wherein the braking surfaces are machined on the inner and outer portions using a chip producing process.

33. A disc brake assembly substantially as herein described with reference to the accompanying drawings.

34. A brake sub assembly substantially as herein descrridh, ith reference to the accompanying drawings. a I o* *o o *o C \WNWORDSIMONESYDNEY13079SP.DOC