GB1335581A - Brakes - Google Patents

Abstract

1335581 Full-face disc brakes H KLAUE 19 April 1971 [18 April 1970 28 July 1970 7 Sept 1970 (2) 8 Oct 1970] 26871/71 Heading F2E Using Fig. 1 as an example, the invention provides a braking assembly comprising two opposing inner faces of a fixed housing 1, 2, two annular brake plates 4, 5 each keyed to a shaft 3 to be braked, two annular brake rings 6, 7, rotationally fixed but axially movable, and urged inwards by connecting pull-off springs 19, and a ball-and-inclined-ramp operating means 10 to 12. As shown in Fig. 1, both operating rings 10, 11 are rotatable, and each is separated from its adjacent brake ring by a row of ball bearings 8, 9, but variants on this are described below. In all cases, the balls 12 may be replaced by rollers, and where bearings 8, 9 are provided they are preferably located radially inwardly of the rolling elements of the operating means. Also, bearings 8, 9 need not be ball bearings. Fig. 2 is a cross-section of Fig. 1, and shows how both operating rings 10, 11 are rotated by a pull rod 15 acting through toggle links 13, 14, the pull rod in turn being raised by clockwise rotation of an arm 18 from the position shown to apply the brakes. In consequence, operating rings 10, 11, are urged outwards, forcing brake rings 6, 7 into contact with brake plates 4, 5, and they in turn into contact with the inner faces of the housing. The brake plates each have friction linings on at least one side; as shown, both sides have them. Fig. 2 also shows some of the ball bearings 9. In Fig. 6, one operating ring of the ball-andinclined-ramp operating means is mechanically actuated by a pull rod 75, while the other is fluid-pressure-operated by a piston 78 in a cylinder 77. The piston includes a rod 79 carrying an expander ring 80. If permissible brake clearance is exceeded, during operation expander ring 80 bears against the inside of a cap 83 on a sleeve 81 fixed to the cylinder, the rod 79 is thereupon drawn slightly through the expander ring, and upon brake release the piston is retained in its new release position by contact of bearer ring 80 with the end of sleeve 81. In Fig. 5 (not shown), which is a variant of Fig. 6, the slack-adjusting device is omitted from the fluidpressure operator, and a manually-operable slack-adjusting device is included in the mechanical actuator (as in Fig. 8 below). In Fig. 8, one of the two operating rings, 109, has outwardly extending lugs 109 1 each of which engages in a slot 104 1 , so that this ring is axially slidable but is not rotatable; ball bearings are not provided between this ring and its adjacent brake ring 107 in this embodiment. The other operating ring 110 has a lug 110 1 to which a pull rod 114 is coupled. A sleeve 115 having internal threads of opposite hand provides for manual slack-adjustment. The slots 104 1 are also used in this embodiment to engage lugs 107 1 and 108 1 on the corresponding brake rings 107, 108, to permit the "axial-only" movement. In Fig. 10 both operating rings are again rotatable and two sets of ball bearings are provided; only one of the operating rings is connected to a mechanical pull-rod, as shown. Each of the brake rings 157 or 158 is prevented from rotating by a series of spring steel straps 162 or 163, anchored to the casing at 164; these straps restrain the brake rings from circumferential movement in the principal (counterclockwise) direction. Clockwise movement is prevented by projections 151 1 on the casing. The brake plates 154, 155, are here splined to the exterior of a sleeve 153 which is in turn splined interiorly to the exterior of shaft 152. Fig. 13 resembles Fig. 10 but includes fluidpressure actuation of the other operating ring at 206 2 , 217 to 219. Also, axial movement of brake ring 207 is provided for by lugs 207 1 having apertures 207 2 each engaging a pin 215 supported at its opposite ends in depressions in the housing wall. Brake ring (208) (not shown) similarly engages the same pins 215.