Patent GB-1166948-A (GB)
Title: Motor Vehicle Brakes
IPC: F16D55/226
Filed: 1967-03-17
Abstract: 1,166,948. Automatic brake wear adjusters; disc brakes. FORD MOTOR CO. Ltd. 17 March, 1967 [24 May, 1966], No. 12516/67. Heading F2E. An automatic brake wear adjuster, particularly for a disc brake, comprises a cylinder containing a brake-actuating piston and at least a part of a screw-and-nut type adjuster assembly, a stressed spring acting between a fixed part and the piston through the assembly and, by virtue of its stress, tending to rotate a threaded member of the assembly to adjust the release position of the piston, and means whereby on increase of fluid pressure in the cylinder to effect brake actuation relative movement in one direction occurs between the assembly and the piston to increase the stress of the spring, and on release of fluid pressure the stress in the spring effects relative movement in the opposite direction, the relative movement in one of the directions, e.g. on brake release, effecting rotation of the threaded member to adjust the release position of the piston. In one embodiment, Figs. 1 and 3, the adjuster assembly 102 (Fig. 3) consists of a threaded member 104 which is secured to the piston 36 of a floating- caliper type disc brake including a caliper housing 32 which is bored to receive the piston, a threaded element 106 in the form of a sleeve threadedly engaging the member 104, a rod 56 extending through a sealed opening in a closure cap 88 whereby it can be engaged by an alternative manual brake applying means in the form of a lever 50, the lower end of the rod being enlarged and seating in a recess 110 of the sleeve 106 to normally engage a shoulder 112, and a pawl 118 which comprises a pawl arm 122, pivoted on a pin 120 carried by the rod 56, and a stressed spring 128 bearing against the closure cap 88 and against arm 130 of the pawl so that an abutment arm 124 of the pawl bears against the cap 88 to determine the position of the arm 122. When fluid pressure in the cylinder increases, piston 36 is moved towards an annular disc 22 to apply an associated brake pad 42, causing a pad 40 carried by a yoke 34 of the caliper housing to be applied also by reaction through the housing. The rod 56, however, does not follow the piston, since pressure acting via a passage 114 in the sleeve 106 on its lower end moves it in the opposite direction, increasing the stress of the spring 128 and pivoting the pawl arm 122 in a direction to ride over one or more teeth on a ratchet wheel 108 formed integrally with the sleeve 106, should adjustment be necessary. Thus, on brake release, opposite pivotal movement of the arm 122 is effected by the stress in the spring 128 and this rotates the sleeve 106 to effect the necessary adjustment. During a manual brake application, effected through the action of a cable 62 on the lever 50 causing an abutment 54 on the latter to engage the rod 56, additional stressing of the spring 128 does not occur and, owing to the increased friction between the threads of the member 104 and sleeve 106, the spring is unable to rotate the pawl to effect adjustment. Fig. 1 shows the general arrangement and the means for guiding the caliper housing for axial movement which comprises a bracket 26 of generally T form, each arm of the T being in the form of a pair of opposed cylindrical members providing channels (70, 72, Fig. 2, not shown) for the reception of guide rods (78, 80) secured in place by pins (82, 84) along which slide opposed cylindrical members formed with corresponding channels (74, 76) and provided on leg portions of the housing 32, from which the yoke 34 extends. In a second embodiment (Figs. 4 and 5, not shown), the pawl (118<SP>1</SP>) has a pair of arms (122<SP>1</SP>a), (122<SP>1</SP>b) engaging opposite sides of aratchet formed along the length of the member (104<SP>1</SP>) which is formed as a sleeve, the sleeve 106 of the first embodiment being replaced by a threaded extension (106<SP>1</SP>) of the rod which extends through the cap (88<SP>1</SP>). In this case the whole of the adjuster assembly moves in the opposite direction to the piston (36<SP>1</SP>) during a fluid pressure brake application to increase the stress of spring (128<SP>1</SP>) which has a pair of limbs each bent such as to act between the cap and the pawl. The operation is otherwise similar to that of the first embodiment. In a third embodiment, Fig. 6, the pawl 118<SP>11</SP> is pivoted on a pin 120<SP>11</SP> carried by the piston 36<SP>11</SP> instead of the rod, the latter providing the threaded element 106<SP>11</SP> as in the second embodiment. Threaded member 104<SP>11</SP> carries a ratchet wheel 108<SP>11</SP> which is engaged by pawl arm 122<SP>11</SP> whose position is determined by the engagement of a reversely bent section of the spring 128<SP>11</SP> with arm 124<SP>11</SP> of the pawl, one end of the spring adjacent this section being engaged with member 104<SP>11</SP> and the other end of the spring being anchored in the pawl arm 122<SP>11</SP> after being passed around the pin 120<SP>11</SP>. In operation, the whole of the adjuster assembly remains stationary while the piston 36<SP>11</SP> moves to apply the brake, since the flattened upper end 146 of the rod engaged in bearing 144 carried by the lever 50<SP>1</SP> is held against movement by the abutment of lever 50<SP>1</SP> against boss 138 of cap 88<SP>11</SP>, the spring 128<SP>11</SP> being stressed as a result and operating the pawl as in the previous embodiments.