Improvements relating to disc brakes

Abstract: A disk brake comprising a brake housing (1) which straddles a braking disc (3) and is slidably mounted on a torque taking member (5) which carries a directly actuated and an indirectly actuated friction pad assembly (25; 29) located on opposite side faces of the braking disc (3). The brake housing (1) is slidable towards and away from the braking disc (3) under the action of an actuator mechanism (13) which is housed in part of the brake housing (1) on one side of the braking disc (3). The actuator mechanism (13) comprises a pair of tappets (15; 17) which can engage against the directly actuatable friction pad assembly (25), the tappets (15; 17) being axially slidable towards the braking disc (3) by a lever and eccentric arrangement (27). One end region of the lever (81) has two lateral extensions (87), each extension (87) forming a part cylindrical bearing surface (89) which is supported on a bearing seat (93) within the brake housing (1). A groove (95) extends transversely of the lever between the lateral extensions (87), the groove (95) being eccentric relative to said part cylindrical bearing surfaces (89) and housing a force transmitting member (97) towards each end region thereof. Each force transmitting member (97) engages a respective tappet (15; 17). An intermediate member (99) located in the groove between the two force transmitting members (97) serves to correctly position the force transmitting members (97) with respect to the tappets (15; 17) and carries a gear drive (73) which engages with an adjuster mechanism which can operate to adjust the length of the tappets (15; 17) as necessary.

Description: The present invention relates to a disc brake for use on a motor vehicle. More particularly, the present invention relates to a disc brake which comprises a fixed torque taking or carrier member which straddles a rotatable disc and carries both a directly and an indirectly actuated friction pad assembly. A brake housing overlies the torque taking member and is guided for sliding movement towards and away from the disc by guide pins which are fixed to the torque taking member and which are slidable in openings arranged in the brake housing in a conventional manner. The brake housing comprises a main body portion which contains an actuator mechanism, and a bridge section integral therewith ie. the bridge section is bolted to the main body portion or integrally cast therewith so as to be of unitary construction. The bridge section has an opening arranged radially of the disc, through which the friction pad assemblies can be inserted and removed from the torque taking member. The present invention relates more specifically to a disc brake wherein the actuator mechanism comprises at least one, but preferably two tappets which are axially movable towards the brake disc to engage and press the directly actuated friction pad assembly against one side of the braking disc, the brake housing reacting and sliding on the said guide pins to apply the indirectly actuated friction pad assembly to the other side of the braking disc. Actuation of the brake is by way of a lever and eccentric arrangement wherein the eccentric arrangement engages the said tappets, pivotal movement of the lever causing the eccentric arrangement to move the tappets towards the braking disc. There is known from WO 97/22814 a disc brake construction which uses an actuating lever arrangement having a cam section with a part cylindrical curved surface and a part cylindrical channel with an elongate cylindrical force transmitting member located therein and being parallel to the longitudinal axis of the said part cylindrical surface, and having opposite end regions which are located in recesses formed in the lever at opposite ends of said channel to thus retain the force transmitting member in position on the lever. The cam section engages a mating curved support surface on a cover plate and is pivotal about said support surface, the lever and cover plate forming a modular assembly for a disc brake, the cover plate being, secured to a clamp member of a disc brake, the force transmitting member then engaging a tappet which can exert force on a friction pad when the lever is pivoted about the support surface. In the above described type of disc brake certain problems occur in known constructions and it is the aim of the present invention to seek to overcome these problems to improve performance, life and ease of manufacture. According to the present invention there is provided a disc brake comprising a brake housing which straddles a braking disc and is slidably mounted on a torque taking member which carries a directly actuated and an indirectly actuated friction pad assembly located on opposite side faces of the braking disc, the brake housing being slidable towards and away from the braking disc under the action of an actuator mechanism which is housed in part of the brake housing on one side of the braking disc, the actuator mechanism comprising a pair of tappets which can engage against the directly actuatable friction pad assembly, said tappets being axially slidable towards the braking disc by a lever and eccentric arrangement, one end region of the lever having two lateral extensions, each extension forming a part cylindrical bearing surface which is supported on a bearing seat within the brake housing, a groove extending transversely of the lever between the said lateral projections, said groove being eccentric relative to said part cylindrical bearing surfaces and housing a force transmitting member towards each end region thereof, each force transmitting member engaging a respective tappet, an intermediate member located in the groove between said two force transmitting members serving to correctly position said force transmitting members with respect to the tappets and carrying a gear drive which engages with an adjuster mechanism which can operate to adjust the length of the tappets as necessary. Preferably the groove is of part cylindrical configuration with the force transmission members being cylindrical members, the intermediate member being likewise cylindrical with the gear drive projecting laterally from the outer surface thereof. The groove may be semi-circular in transverse cross section or less than a semi-circle in transverse cross section, in which case the force transmitting members and the intermediate member can merely be located laterally within the groove during installation. Alternatively, if the groove is larger than a semi-circle, the various members have to be axially slid into the groove. Whilst the force transmitting members are rotatable within the groove and are axially retained in position preferably by the intermediate member and the retaining projection of each bearing seat member as described hereabove, the intermediate member is preferably fixed in the groove against rotation and/or axial movement by the surface of the lever adjacent the groove being staked ie. deformed, at spaced locations along the axial length of the groove. Alternatively, the intermediate member may be axially retained in the groove, eg. by the force transmitting members, though rotatable therein to a limited extent, the rotational limit being defined by the gear drive engaging the sides of the groove, this limited rotation possibly providing for the required lost motion in the adjuster mechanism. The lever and lateral extensions are preferably cast with the groove required to locate the force transmitting members and intermediate member, being machined in one operation. Whilst the lever and lateral extensions are preferably manufactured from cast steel, the intermediate member could, if desired, be manufactured from any other suitable metal, eg. even a plastics type of material. The above construction provides an improved weight reduced lever and eccentric arrangement which is easy to manufacture and arranged to advantageously provide a drive mechanism to the adjuster mechanism. The present invention will now be further described, by way of example, with reference to the accompanying drawings, in which:- Fig. 1 is a partially cut-away view of one embodiment of a disc brake constructed according to the present invention; Fig. 1A is a cross sectional view of the brake shown in Fig. 1; Fig. 1B is a cross-sectional view of part of a modified embodiment of the present invention; Fig. 2 is a partially cut-away view of a further embodiment of a disc brake constructed according to the present invention; Fig. 3 is a partially cut-away view of a still further embodiment of a disc brake constructed according to the present invention; Fig. 4 is a cross sectional view of part of a still further modified embodiment of the present invention; Fig. 5 is a cross sectional view taken along line A-A in Fig. 4; Fig. 6 is a view of the brake with the cover plate removed, illustrating the mirror image duplication of available recesses; Fig. 7 is a perspective, partially cut-away view of a bearing seat member; Fig. 8 is an inverted plan view of the bearing seat member of Fig. 7; Fig. 9 is a rear view of a lever arrangement as utilised in the embodiments of Figs. 1, 2 and 3; Fig. 10 is a front view of the lever in Fig. 9; Fig. 11 is a side view of the lever of Figs. 9 and 10; Fig. 12 is a plan view of the intermediate member used with the lever of Figs. 9 to 11; Fig. 13 is an end view of the intermediate member of Fig. 12; and Fig. 14 is a cutaway partial view of any one of the embodiments of Figs 1 to 3, illustrating the seal assembly of the present invention, in enlarged detail. Referring to the embodiment of the present invention illustrated in Figs. 1 and 1A of the accompanying drawings, the brake basically comprises a brake housing generally designated 1, which straddles a braking disc 3 and is slidably mounted on a torque taking member 5 by virtue of guide pins (not illustrated) in a conventional manner. The brake housing 1 comprises a main body section 7 which is bolted to a bridge section 9. Alternatively, the main body section and the bridge section can be integrally cast as a unitary construction, the main body section having a cavity or recess 11 within which a brake actuator mechanism generally designated 13 is located, the cavity or recess in the brake housing being open towards the braking disc 3 to allow for the location of the actuator mechanism 13 during manufacture and assembly. The actuator mechanism 13 comprises a pair of tappet assemblies 15, 17 which are parallel to each other and which extend through bearing apertures 19, 21 provided in a cover plate 23 which is secured to the brake housing 1 and which closes off the said cavity/recess 11, each tappet assembly 15, 17 being engageable with a directly actuated friction pad assembly 25 under the action of a lever and eccentric arrangement 27. Pivotal movement of the lever 27 causes the tappet assemblies 15,17 to move towards the braking disc 3 to engage the directly actuatable friction pad assembly 25 and press this friction pad assembly 25 against one side of the braking disc 3. Continued pressure causes the brake housing 1 to slide on the guide pins relative to the torque taking member 5 and braking disc 3, with the bridge section 9 pressing on an indirectly actuatable friction pad assembly 29 which engages the opposite side of the braking disc 3. Each tappet assembly 15, 17 comprises an elongate female part 31 which has an enlarged head region 33 which can engage or act upon the directly actuatable friction pad assembly 25. The other end region 35 of said female part 31 has a blind bore 37 which extends axially through the said female part 31. Threadedly interengaged in said blind bore 37 is a male part 39 of each tappet assembly 15, 17, the outer end region of said male part 39 being formed with an enlarged head region 41 on which the lever and eccentric arrangement 27 acts. As evident in Fig. 1 of the accompanying drawings the cover plate 23 is provided with a cylindrical extension 43 projecting perpendicularly therefrom and into the cavity 11 of the brake housing 1, the inner wall 143 of this cylindrical extension 43 forming a supporting bearing surface for the outer wall of the female part 31 of each tappet assembly 15, 17, the cylindrical extension 43 supporting said female part 31 for the majority of its length and thus limiting, if not preventing, tilting of the female part 31 of the tappet assembly 15,17 in its bearing support. Further, the enlarged head region 41 of the male part 39 of each tappet assembly 15,17 has a cylindrical lip extension 45 which extends in the same direction as the threaded shaft of the male part 39, this cylindrical lip 45 engaging and being carried upon the outer surface of the cylindrical extension 43 of the cover plate 23. Thus the cylindrical head 41 of the male part 39 of each tappet assembly 15, 17 is positively carried by the cylindrical extension 43 of the cover plate 23, thereby resisting any side forces which may be applied by virtue of the lever and eccentric 27 and limiting, if not preventing, any tilting of the tappet assemblies 15, 17 with the resultant advantageous removal or minimising of tapered wear on the friction pad assemblies 25, 29, and improving brake and adjuster efficiency. As seen in Fig. 1 of the accompanying drawings, the female part 31 of each tappet assembly 15, 17 is keyed as at 47 for solely axial movement within the cylindrical projection 43 of the cover plate 23, rotation of the male part 39 of each tappet assembly 15,17 thus solely causing axial movement of the female part 31 thereof. Further, the cylindrical lip 45 carries an annular washer 49 against which one end of a coiled spring 51 engages, the other end engaging the cover plate 23. This spring 51 thus presses the male part 39 of each tappet assembly 15, 17 against the lever and eccentric arrangement 27. To produce axial adjustment of each tappet assembly 15, 17 rotation of the male part 39 is required and this is effected via teeth 53 provided on the outer surface of the cylindrical lip 45, a gear wheel 55 of an adjuster mechanism 57 engaging the teeth 53 on the respective male parts 39 of the respective tappet assemblies 15, 17. The adjuster mechanism 57 is likewise carried in a recess 59 defined by a cylindrical projection 61 of the cover plate 23, this cylindrical support 61 positively retaining and securing the position of the adjuster mechanism 57 within the brake housing 1, and thereby ensuring improved positioning with respect to the male part 39. Additionally, further recessed projections (see Fig. 6) can be provided ie. cast in the cover plate 23, to facilitate positive retention and positioning of various mechanisms eg. a pad wear sensor mechanism. Preferably, such recessed projections are provided in a mirror image duplication (see ghosted circles 44,46 in Fig. 4) so that during assembly of the brake the cover plate 23 will readily fit all of the desired features whichever way it is located. The adjuster mechanism 57 comprises the gear wheel 55 which is fixedly mounted on core part 63 which is freely rotatably mounted on rotatable shaft 65, a further cylindrical core part 67 being fixed on said shaft 65 against rotation relative thereto, with a wrap spring 69 engaging the outer surfaces of said core parts 63, 67. Further, to facilitate rotation of said shaft 65, a gear wheel 71 with axially extending teeth on its perimeter is secured on said shaft 65 with a degree of rotational clearance between the gear wheel 71 and the shaft 65 defining the normal brake slack, said axially extending teeth meshing with a gear drive 73 forming part of the lever and eccentric arrangement 27. Thus, pivotal movement of the lever and eccentric arrangement 27 causes the gear drive 73 to take up clearance with the axially extending teeth of the gear wheel 71, sufficient pad wear resulting in the gear drive 73 being rotated far enough to rotate the gear wheel 71 and rotatable shaft 65, causing the wrap spring 69 in this direction of rotation, to secure the two core parts 63,67 together, resulting in the gear wheel 55 rotating the male parts 39 of the respective tappet assemblies 15, 17 with the female parts 31 thus moving axially relative thereto to adjust the length of the respective tappet assemblies to take account of pad wear, return motion of the lever and eccentric arrangement 27 being released from the respective tappet assemblies via the wrap spring 69 which provides a lower drag torque between the core parts 63, 67 in the reverse direction of rotation. In a modified form of the disc brake constructed according to the present invention and shown in Fig. 1B, wherein the reference numerals used in Fig. 1 are again used to indicate equivalent parts, the free end region 43' of each cylindrical projection 43 has an enlarged internal diameter within which the enlarged diameter head region 41 of the male part 39 of a tappet 15,17 engages, the inside wall of said free end region 43' thus supporting the male part of the tappet. This enlarged head region 41 is provided with the teeth 53 which mesh with the adjuster mechanism via an opening 43" in the wall of the said free end region, the spring 51 being likewise within the cylindrical projection between the enlarged head region 41 and a shoulder formed by the stepped bore in the cylindrical projection 43. In a further modified form of the disc brake of the present invention as shown in Fig. 2 of the accompanying drawings, wherein the reference numerals used in Fig. 1 are again used to indicate equivalent parts, the said cylindrical extensions 43 of the cover plate 23 are reduced in axial length as compared to those of the Fig. 1 construction, with a bearing cylindrical liner 75 being secured therein and extending for the major part of the length of the female part 31 of each tappet assembly 15,17, the cylindrical lip 45 of the male part 39 of each tappet assembly 15, 17 engaging over the free end region of the respective bearing liners 75. By this construction, the bearing liner 75 can be made of a more suitable, usually more expensive bearing material as opposed to the usual cast material construction of the cover plate 23, thereby minimising the cost of construction. In a still further embodiment of the present invention, as illustrated in Fig. 3 of the accompanying drawings, wherein the reference numerals used in Fig. 1 are again used to indicate equivalent parts, whilst the cylindrical extensions 43 of the cover plate 23 are as provided in the embodiment of Fig. 1, the cylindrical lip 45 on the enlarged head region 41 of the male part 39 of the respective tappet assemblies 15, 17, is formed by an annular member 77 which is secured around the enlarged head region 41 of each male part 39, this annular member 77 forming the required cylindrical lip which engages over the cylindrical extension 43 of the cover plate 23 to support the male part 39 of each tappet assembly 15,17, the outer surface of each annular member 77 being provided with appropriate teeth 79 which mesh with the gear wheel 55 of the adjuster mechanism 57. This modified construction can provide advantages in manufacture particularly with the choice of materials bearing in mind wear etc. with regard to the meshing of the teeth 79 with the gear wheel 55 of the adjuster mechanism 57. Whilst the male and female parts 31, 39 in each of the embodiments of Figs. 1, 2 and 3 of the accompanying drawings are keyed together by an axially extending spline/groove (see 47 in Fig. 1), Figs. 4 and 5 of the accompanying drawings show a modified form of the present invention wherein the female part 31 of each tappet assembly 15, 17 is keyed for solely axial movement within the bearing projection 43 of the cover plate 23, by the outer profile of the transverse cross section of the female part 31 being trilobal and being located in a complimentary trilobal transverse cross section bearing aperture 43' in the bearing projection 43 of the cover plate 23. Thus the female part 31 is an axially slidable fit on the bearing aperture 43' but cannot be rotated relative thereto, rotation of the axially secure male part 39 thereby causing axial movement of the female part in the bearing aperture 43'. Further the trilobal cross sections of the two tappet arrangements 15, 17 are arranged in the same orientation with the apex 43" of one lobe of each trilobal cross section being directed towards the centre of rotation of the brake disc 3 as shown in Fig.4 of the accompanying drawings. By this construction the tendency for the tappets 15, 17 to bind and/or tilt in the bearing apertures 43', as the brake experiences torque during brake applications, is minimised. This trilobal construction is considered easier to manufacture than, for example, a splined arrangement such as shown at 47 in Fig. 1, as it can be formed by a simple forging process on said female part 31. Also if the bearing aperture 43' is formed by a bearing sleeve 75' secured to the cover plate 23, as shown in Figs. 4 and 5, the trilobal construction is easily formed with the sleeve 75' being manufactured by way of sintering and therefore requiring a minimum amount of finishing. If desired, the sintered bearing 75' may be cast into the die cast cover plate 23. With regard to the lever and eccentric arrangement 27 in each of the embodiments of Figs. 1, 2 and 3 of the accompanying drawings as best seen in Figs. 9 to 13, this comprises an elongate lever 81, one upper end region 83 of the lever 81 being engageable by actuating means such as a pneumatic actuator, whilst the other, lower end region 85 has two opposite directed lateral extensions 87 which effectively form an operational bearing shaft. To explain, opposite end regions of this operational bearing shaft are formed with part cylindrical bearing surfaces 89 which, in use, are supported on bearings 91 carried on like curvature bearing seat members 93 located in the brake housing 1, as described hereinbelow. Eccentric to the centre of curvature of the respective curved bearing surfaces 89 of the operational bearing shaft, and generally opposite to said bearing surfaces, is an elongate groove 95 which is machined along the length of said operational bearing shaft. This groove 95 has a part cylindrical configuration which is less than semi-circular in transverse cross section. Alternatively, if desired, the groove 95 may have a transverse cross section which is larger than a semi-circle. Cylindrical force transmitting members 97 which are of a complimentary diametrical dimension to the said groove 95, are located at opposite end regions of the groove 95 with an intermediate member 99 located therebetween, the intermediate member 99 preventing axial movement of the force transmitting members 97 towards each other. The gear drive 73 previously referred to is a lateral extension of this intermediate member 99 and the intermediate member 99 is secured against rotation or axial movement in the groove 95 by adjacent regions of the operational bearing shaft being deformed ie. staked, adjacent to the edge of the groove 95. Alternatively, the intermediate member 99 may be allowed to rotate to a limited degree, rotation being limited by the lateral gear drive 73 engaging the edges of the groove 95, this limited rotation providing for the required lost motion in the adjuster mechanism 57 to which the gear drive 73 is meshed. Whilst the intermediate member 99 is made of cast steel it may alternatively, if desired, be made of any suitable other metallic material or even a plastics material. As referred to hereabove the curved bearing surfaces 89 at opposite end regions of the operational bearing shaft are supported on bearings 91 which are mounted on complimentarily curved surfaces 101 in bearing seat members 93 which are themselves located in appropriate recesses 109 in the bottom face of the cavity 11 in the brake housing 1. These bearing seat members 93 are best illustrated in Figs. 7 and 8 wherein it will be seen that each bearing seat member 93 presents a curved bearing support surface 101, at one end of which is provided a retaining section 105. As evident from Figs. 1, 2 and 3, these retaining sections 105 extend over the ends of the groove 95 in the operational bearing shaft to hold the force transmitting members 97 in the respective end regions of the said groove 95. As shown in Fig.8 the base 107 of each bearing seat member 93 is generally of circular/cylindrical configuration and is freely rotatably located in a complimentary recess 109 in the base of the cavity 11. Thus, during installation, when the bearing operational shaft and bearings 91 are located on the respective bearing seat members 93, the bearing seat members 93 rotate in their respective recesses 109 to become accurately and correctly aligned with each other for subsequent use. In a modified form of construction, the base of each bearing seat member 93 is shaped eg. tapered, so as to overly the edges of the recesses 109 in the base of the cavity 11 in the brake housing 1. Thus, whilst the respective bearing seat members 93 can be generally located in position, when the lever and eccentric arrangement 27 is located on the respective bearing seat members 93, the bearing seat members 93 rotate to correctly and accurately align with each other, and then on initial use of the brake, the bearing seat members 93 are deformed into the respective recesses 109 to firmly and positively secure the bearing seat members 93 as an integral part of the brake housing 1. Alternative possible shapes and configurations are of course possible for the bearing seat members 93 and the recesses 109 to provide for this positive and secure attachment of the bearing seat members 93 to the brake housing 1. Further these bearing seat members 93 facilitate manufacture as it would be difficult to machine appropriate bearing support surfaces 101 in the base region of the cavity 11 in the brake housing 1 without the provision of an outer cover plate, or a lateral opening which would then require to be sealed. Also, by the provision of separate components as bearing seat members 93, a more suitable material can be selected for the construction of the bearing seat members 93 without the need for the whole brake housing 1 to be manufactured from the selected material. Thus manufacturing costs can be reduced in two different ways by virtue of the provision of the separate bearing seat members 93. Further, as evident from Figs. 1, 2 and 14 of the accompanying drawings, a positive and secure seal assembly 110 is provided for each tappet assembly 15, 17. Each such seal assembly 110 comprises an annular flexible boot 111, one end 113 of which is beaded and resiliently and firmly engaged in an annular recess 115 around the head region of the female part 31 of the tappet assembly 15,17. The other end region of the flexible boot 111 is likewise beaded 117 and engages between an upper surface of the cover plate 23 and a parallel surface of an annular retaining member 118 which is of stepped configuration in transverse cross section. A further lip seal 119 is secured eg. bonded, to the inner edge of the retaining member 118 so as to project inwardly thereof. A middle region of this retaining member 118 is generally cylindrical and engages in an enlarged diameter region 121 at the mouth of the bearing aperture 19 in the cover plate 23, through which the tappet 15, 17 passes, the retaining member 118 thus correctly positioning the inwardly directed sealing lip 119 and the flexible boot 111. With the above sealing assembly 110 construction, assembly is facilitated and manufacturing costs thereby reduced, the annular lip seal 119 is secured eg bonded, coaxially with the annular retaining member 118 which is preferably made of metal. During construction of the brake, the combined lip seal 119 and retaining member 118 are fitted into the enlarged end region 121 of the bearing aperture 19, prior to the tappet 15,17 being inserted in the bearing aperture 19, the retaining member 118 being an interference fit in the enlarged end region 121 of the bearing aperture 19. Then the tappet 15,17 with the flexible boot member 111 secured to the head region 33 of the female part 31 of the tappet 15,17, is inserted through the lip seal 119 and thus the bearing aperture 19, the flexible boot member 111 then being secured between the retaining member 118 and an adjacent surface of the cover plate 23. In an alternative embodiment (not illustrated) the flexible boot member 111 is also secured eg bonded, to the retaining member 118 so that the boot member 111, lip seal 119 and retaining member 118 form a unitary construction, the sealing assembly 110 can be attached to the female part 31 of a tappet 15,17 assembly with the bead 113 being securely engaged in the annular recess 115 in the head region 33 of the said female part 31, after the retaining member 118 and sealing lip 119 have been slid axially along the outer surface of the said female part 31. Then, the female part 31 of the tappet assembly 15, 17 can be inserted into the bearing aperture 19 together with the seal assembly 110, and the cylindrical portion of the retaining member 118 can be pressed into the enlarged diameter mouth region 121 of the bearing aperture 19, this being an interference fit, to thus positively locate the sealing lip 119 and the flexible boot 111. The above construction of disc brake has considerable performance advantages together with advantages respect of the ease of assembly ie. reduce manufacturing costs.

Claims: A disk brake comprising a brake housing (1) which straddles a braking disc (3) and is slidably mounted on a torque taking member (5) which carries a directly actuated and an indirectly actuated friction pad assembly (25; 29) located on opposite side faces of the braking disc (3), the brake housing (1) being slidable towards and away from the braking disc (3) under the action of an actuator mechanism (13) which is housed in part of the brake housing (1) on one side of the braking disc (3), the actuator mechanism (13) comprising a pair of tappets (15; 17) which can engage against the directly actuatable friction pad assembly (25), said tappets (15; 17) being axially slidable towards the braking disc (3) by a lever and eccentric arrangement (27), one end region of the lever (81) having two lateral extensions (87), each extension (87) forming a part cylindrical bearing surface (89) which is supported on a bearing seat (93) within the brake housing (1), a groove (95) extending transversely of the lever between the said lateral extensions (87), said groove (95) being eccentric relative to said part cylindrical bearing surfaces (89) and housing a force transmitting member (97) towards each end region thereof, each force transmitting member (97) engaging a respective tappet (15; 17), characterised by an intermediate member (99) located in the groove between said two force transmitting members (97) serving to correctly position said force transmitting members (97) with respect to the tappets (15; 17) and carrying a gear drive (73) which engages with an adjuster mechanism which can operate to adjust the length of the tappets (15; 17) as necessary. A disc brake as claimed in claim 1, in which the groove (95) is of part cylindrical configuration, with the force transmission members (97) being cylindrical. A disc brake as claimed in claim 2, in which said intermediate member (99) is cylindrical, with a gear drive (73) projecting laterally from the outer surface thereof. A disc brake as claimed in claim 3, in which the intermediate member (99) is rotatable in the groove (95), with rotation being limited by the gear drive (73) engaging the sides of the groove, this limited rotation providing a lost motion mechanism for an adjuster mechanism (57) of the brake. A disc brake as claimed in claim 3, in which the intermediate member (99) is secured against rotation in the groove (95). A disc brake as claimed in any of claims 1 to 5, in which the intermediate member (99) is made of a plastics material.

Inventors: HEINLEIN CARL EDWARD, JACKSON JONATHAN LESLIE CHRIST, TROTT PHILLIP LEONARD, HEINLEIN, CARL EDWARD, JACKSON, JONATHAN LESLIE CHRISTOPHER, TROTT, PHILLIP LEONARD
Applicants: MERITOR AUTOMOTIVE INC, MERITOR AUTOMOTIVE, INC.
Application year: 1998
Main classification: F16D65
IPC codes: F16D65, F16D55