FR2493441A1 - DISC BRAKE WITH SLIDING SADDLE WITH MECHANICAL CONTROL - Google Patents

Abstract

THE DISC BRAKE INCLUDES A SLIDING SEAT 1, A BRAKE DISC 6, BRAKE LINING BRACKETS 2, A DRIVE SHAFT 7, A SHAFT COLLAR 9, OBLIQUE BEARING TRACKS 10, 12, A BEARING BUSH 13, AN ADJUSTING DEVICE INCLUDING IN PARTICULAR AN ADJUSTING NUT 14, A CLAMPING SCREW 15 AND A BEARING BUSH 13. THE DRIVE SHAFT 7 IS APPLIED TO THE SLIDING SEAT 1 THROUGH AN AXIAL BEARING 27 TO PREVENT AN AXIAL DISPLACEMENT OF THE COLLAR 9 ON THE SIDE FACING THE OBLIQUE BEARING TRACKS 10, 12; THE BEARING BUSH 13 CAN MOVE AXIALLY WITH RESPECT TO THE BRAKE SEAT, BUT CANNOT TURN AND APPLIES TO THE ADJUSTING NUT 14; THE ADJUSTING RING 29 IS MOUNTED SO THAT IT CAN TURN ON AN ADJUSTING NUT AND IS COUPLED TO A CONTROL DEVICE CONSISTING OF A GROOVE 30 AND A TENON 31 RECESSED IN THE GROOVE, WHICH CAUSES ROTATION OF THE RING OF ADJUSTMENT WHEN THE DRIVE SHAFT ROTATES OR THE BEARING RING MOVES AXIALLY AS A RESULT OF THIS ROTATION.

Description

Sliding disc brake with mechanical control This

  The invention relates to a mechanically-controlled disc brake comprising a sliding saddle mounted so as to be able to move transversely to the brake disk and overlies the brake disk, each of the two halves of the saddle carrying a brake lining support.

  with its lining, a control shaft being rotatably mounted

  in one of the halves and having, at its end ending in a box-like shape, a protruding collar

  radially, which is provided on one of its sides with

  of oblique bearings intended to receive balls

  which correspond to oblique bearing paths pre-

  seen on a bearing ring and which serve to transform the

  rotational movement of the control shaft in a displacement

  axial position of a tightening screw on one of the

  brake lining ports, and having a play-catching mechanism which comprises a setting ring coaxial with the clamping screw, placed with the control shaft in

  functional relationship such as when the tree of com-

  has turned at an angle greater than that which corresponds to a determined wear of the brake lining, and that a setting nut connected to this shaft has rotated at the same time by returning to its starting position during the release of the brake , this ring is unscrewed from the clamping screw and

  interferes with the flow of forces transmitted from the

  control knob to the clamping screw.

  In a known disk brake according to the prior art

  German Patent Application Publication No. 2,647,353), the control shaft passes through the bearing ring which bears on the sliding saddle, so that the control shaft, by turning, automatically moves into the axial direction. The movement of axial displacement passes

  the control shaft on the clamping screw because of its

  direct frontal position on the adjusting nut. The adjusting nut is practically disk-shaped, and on both sides there are annular disk-shaped wave springs, each of which

  fixed in relation to the sliding saddle, and enclose the

  adjustment nut between them. On its front side provided with an oblique toothing in the form of saw teeth rests the adjusting ring associated with the control shaft, with a corresponding oblique toothing.

  This known embodiment has important defects

  tives. First, from a construction point of view, it is necessary to take into account the possibility of axial displacement of the control shaft so that it is provided between

  the pivoting lever attached to the control shaft and the saddle

  brake, an elastic sealing liner that can

  sorb not only the oscillating movement of the lever, but also the movement of the lever towards the saddle of the brake. From a functional point of view, it can be objected to the fact that, at the beginning of the oscillating movement of the control shaft, the friction resistance of the shaft with respect to the adjusting nut which then rests on it, resistance which is still small, must allow a relative rotation between the tree

  and the adjusting nut. This results in a relative shift

  uncontrolled movement of the adjusting ring with respect to

  adjustment nut. This relative rotation is superimposed, in case of braking, to an additional rotation due to an excessive oscillation angle of the control shaft after wear of the brake lining. When releasing the brake, the adjusting nut must advance on the clamping screw

  from a given distance. But this distance can not be

  determined in advance because it depends on the reports

friction.

  The object of the present invention is to provide a

  disc brake according to the already known technique, which is

  thanks to a particularly perfect setting despite its simple construction, ease of

its small size.

  The disk brake according to the invention, with which the ob-

  mentioned above, is characterized in that the control shaft is applied to the sliding saddle by

  through an axial bearing to prevent movement

  axial direction of the collar on the side facing the oblique bearing paths, in that the bearing ring can move axially with respect to the saddle of the brake, but can not turn and is applied to the adjusting nut made in the form of a sleeve, and in that the adjusting ring is rotatably mounted on the adjusting nut and is coupled to a control device, consisting of a groove and a pin or tenon embedded in the groove, which causes the adjusting ring to rotate when the control shaft rotates or the bearing ring

  moves axially as a result of this rotation.

  The invention is therefore based on the discovery of the fact

  that exactly pre-determined operating conditions

  the brake shaft can be reached when the control shaft is prevented from moving axially and at the same time it is ensured that the bearing ring can move axially to drive the clamping screw through the axle. intermediary of the adjusting nut which rests on the ring, but that the bearing ring can not, however, enter

  in rotation, which would compromise the accuracy of the

  brake application. In addition, the invention is based on the discovery of

  green because the clearance between the post or pin and the groove determines the angle of oscillation or pivoting, within which adjustment or catching of the game can still be caused, and that the moment of adjustment can be

  exactly predetermined accordingly.

  It has been found particularly advantageous in another aspect of the disk brake according to the invention that the adjusting ring rests on an annular edge of the adjusting nut by a substantially conical shaped surface, under the effect of a spring acting axially on the adjusting ring. The use of such a friction cone is related to

  the advantage of progressive adjustment.

  The groove of the device or control mechanism may be directed parallel to the axis of the control shaft and be arranged either in the control shaft or in the adjusting ring. In this case, the pin or pin must be attached either to the adjusting ring or to the control shaft. The groove of the control device can be directed along the axis of the control shaft but also obliquely and be arranged either in the sliding saddle or in the adjusting ring. In this case, the pin or pin must be attached to either the adjusting ring or the sliding saddle. When it is necessary to change the brake lining, or when it is necessary to modify the starting setting of the brake,

  it is necessary to turn the adjusting nut

  from the control shaft. But as the device

  The adjustment device is arranged inside the sliding seat.

  it is not accessible until the completion of the

truction of the control shaft.

  In another advantageous embodiment of the invention, it is therefore provided that the adjustment device is disposed outside the sliding saddle. Thanks to this particularity of construction, one can have access to

  adjusting device, for adjustment purposes, from the outside

  without dismantling work that takes time.

  For the same purpose, it is provided in another embodiment of the invention that the adjusting nut is

  fixed, so that it can not turn, to a piece of pro

  which coaxially traverses the control shaft, and that an adjustment sleeve, associated with the adjusting ring, is connected to the extension piece via a

friction coupling.

  As the adjusting sleeve is associated with the adjusting ring, which in turn is in operative connection with the control shaft, in the normal use of such a sliding saddle disc brake, a rotation of the shaft of control results in a rotation of the adjusting nut. But if necessary, the adjusting nut can be turned from the outside independently of the adjusting shaft, rotating the extension piece to

  with the help of an appropriate tool, so that the force of

  the friction coupling is found in the vaicune

  and that the extension piece rotates relative to the man-

setting chon.

  Other peculiarities, advantages and characteristics

  the invention will emerge from the description which will

  FIG. 1 is a section parallel to the axis of the sliding saddle disc brake according to the invention, in accordance with a first embodiment thereof, FIG. 2 is a sectional view of FIG. FIG. 3 is a schematic top view of a detail of the brake, in the zone referenced by the arrow III of FIG. 1, FIG. a longitudinal section of a second embodiment of the sliding saddle disc brake according to the invention, FIG. 5 represents a detail of the brake according to FIG. 4, in the zone referenced by the arrow V of FIG. FIG. 6 is an axially parallel section of a third embodiment of the sliding saddle disc brake according to the invention, FIG. 7 is a view taken along arrow VII of FIG. shows an adjusting ring, Figure 8 is a view taken 8 is an axially parallel section of a fourth embodiment of the sliding saddle disk brake according to the invention, and FIG. a cross section following the

line X-X of Figure 9.

  As is evident from the drawings, the sliding saddle disc brake shown is comprised of a sliding saddle which covers by its two halves 4 and 5 the brake disc 6 shown in broken trains. The two saddle halves each comprise a brake lining support, which carries a brake lining 3 adjacent to the brake disc 6. In the half 5 of the sliding saddle 1 is mounted a control shaft 7 that can be made turn by means of a lever 8. This control shaft ends with a box-shaped end with a collar 9 projecting radially. This collar is provided on its side which is opposite the lever 8, at least two, and preferably three, oblique raceways for receiving balls 11, which roll other

  part on a bearing ring 13 in rolling paths.

  The mutually corresponding oblique raceways 10 and 12 are arranged on the collar 1 9 or on the bearing ring 13 relative to each other.

  other, so that a running of the tree of com-

  Mande 7 is converted into an axial displacement of the bearing ring 13 and an adjusting nut 145. In this adjusting nut 14 is screwed a clamping screw 15, which rests, by its front end, on a holding member 16 brake pad holder 2. In the transmission of the axial forces from the bearing ring 13 to the sleeve-shaped adjusting nut 14, the latter is provided with: a radially projecting shoulder 17 on which the bearing ring rests. So that the bearing ring can move

  axially under the effect of the control shaft 7 without taking

  part of the rotation of the shaft 7, provision is made

  anti-rotation stif, constituted by a guide groove 18 parallel to the axis and in which is embedded a post or

  guide pin 19 radially crossing the saddle

  This guide post 19 is formed by the end

  a threaded bolt 20 screwed into a threaded hole of the sliding seat 1. For simplicity, this threaded bolt is shown in a position in which its geometric axis is in the plane of section. vertical sliding seat. But in fact, the threaded bolt 20 occupies a position such that the guide pin 19 is angularly offset from the

plane of the figure.

  To prevent rotation of the clamping screw 15 with the adjusting nut 14, the clamping screw 15 is provided in the region of its peg resting on the element 16, with a recess 21 in which recesses a nose 22 of

element 16.

  As can be seen in Figure 1, on the front end of the adjusting nut 14 rests a metal ring 23 which is subjected to the action of a coil spring 24. This spring is supported, by its free end, through

  of a ring 25, on a shoulder of the saddle

  1. An angled pad 26 of resilient plastic material between the sliding saddle 1 and the

  tightening screw 15, protects the control mechanism of the in-

  troduction of foreign bodies, dirt and moisture.

  On the rear side of the collar 9, turned away from the oblique raceways 10, there is provided an axial bearing 27, through which the control shaft 7

  relies on the sliding saddle 1, and this

  of an annular disk 28 which rests on a shoulder

of the sliding saddle 1.

  As shown in Figure 1, on the end of the

  adjusting nut 14 which is turned towards the shoulder 17 is

  mounted, rotatably, an adjusting ring 29.

  This adjusting ring has a groove 30 arranged parallel to the axis. In this groove 30 is embedded a pin 31 which is connected to the control shaft 7 and whose diameter is smaller than the width of the groove, the

  difference representing the game "L". On the outer end

  the adjusting nut 14 is provided with a ring of

  reté 32, which serves to support a corrugated disk 33 acts

  On the adjusting ring 29, under the effect of the corrugated disc 33, the adjusting ring 29 is held by an oblique toothing 34 in the form of saw teeth.

  on the frontal side, in contact with an oblique denture cor-

  35, which is provided on a shoulder of the nut

setting 14.

  The disc brake described above operates as follows

  When the control shaft 7 is rotated through

  8, the balls 11 travel along a track on the oblique raceways 10 or 12, which has the consequence that the bearing ring 13 moves towards the

  brake disc 6. The ring thus causes the adjusting nut

  14 through the shoulder 17, and the clamping screw 15 which is screwed into this nut, which causes an application, through the element 16, the brake lining 3 fixed on the brake pad holder 2, on the brake disc.

  reaction force, the sliding saddle 1 moves axially-

  towards the right with respect to the brake disk 6,

  that finally that the brake lining support which is on the saddle half 4 is also applied on the brake disc 6 by its brake lining 3o During this actuation of the brake, the force of the spring 24 must must be overcome which tends to bring back, during the release of the brake5 all the elements

in their starting position.

  During the rotation of the control shaft 7, its collar

  let 9 leans on the slender saddle! by! 'interme-

  In the pivoting of the control shaft 7, the pin 31 moves in the groove 30 of the adjusting ring 29 by a distance corresponding to the clearance I "L" illustrated in FIG. ! Wear of the filling of

  brake has exceeded a predetermined value, a pivot angle

  The larger the shaft 7 becomes necessary for the tightening of the brake. As a result, the end 31 is applied to the other end of the groove 30 and thus to a drive of the adjusting ring 29, so that the latter turns by

  relative to the adjusting nut 14. When the rotation movement

  the adjusting ring 29 with respect to its adjusting nut 14 passes the width of a tooth of the oblique toothing 34, 35, a tooth of the oblique toothing is located

  jumped. When the elements return after the end of the process

  braking force, the control shaft 7 drives the adjusting nut 14 through the teeth 31 and the adjusting ring 29 with the oblique toothing 34, 35, which is then in engagement with them, so well that the clamping screw 15 is unscrewed from the adjusting nut 14 towards the brake disc 6 by a distance corresponding to the wear of the

  brake lining. In this way, it is provided with a compensation

  sation of the lining wear by automatic adjustment.

  The second embodiment shown in FIG. 4 conforms, in relation to the basic construction, to the embodiment of FIG. 1. The same constituent elements are therefore designated by the same

numerical landmarks.

  This embodiment differs from that of FIG. 1, essentially in that the groove 30a is constructed in the form of an oblique groove, which

  more is still shown in FIG.

  offset by 90 *. The tenon 31a which fits into this oblique groove 30a is, in this case, fixed in the

sliding saddle 1.

  The bearing ring 13 is also in this form

  embodiment, provided with a guide groove 18, in the-

  which is fitted a guide pin 19 crossing radial-

  the sliding saddle. This guide post is cylindrical

  and is provided, in the area of the guide groove, with

  flats 36. On its posterior end, the tenon of

  flats 36. On its posterior end, the tenon

  19 has a radial shoulder 37, which determines

  in conjunction with a corresponding rotation of the hole

  in the sliding saddle that corresponds to it, how far the tenon protrudes from this hole. At the section of the hole which receives the guide pin 19 is connected a larger section, provided with a thread, which is intended to receive a six-hole screw 38 fixing the guide pin. In order to align the flats 36 of the guide pin 19 with respect to the guide groove 18, it is provided, in

  the area of the rotation of the hole in the saddle

  smoothing, a clamping pin 39 which is associated with a slot 40 in -the area of the radial shoulder 37 of the tenon

guidance.

  As shown in Figure 4, in this form of

  the pin 31a, which fits into the groove

  30a, is disposed on the outer end of the guide pin 19 which passes through the guide groove 18 of the bearing ring 13, so that it projects from the guide pin. Also in the embodiment according to FIG. 4, the adjusting ring 29 is subjected to the action of an elastic disk 33. As is clear from FIG. 5, in this case the adjustment ring 29 is press, by a substantially conical surface, on a

  annular edge 42 of the adjusting nut 14.

  To prevent the clamping screw 15 from rotating,

  In the embodiment of FIG. 4, the screw of FIG.

  rage is connected to a ruler 43 which radially and

  which fits into a groove 44 of the brake saddle 1.

  In the second form of re! sation is to be

  described, a rotation of the control shaft 7 also leads to

  also, via the ball I and associated oblique raceways, a dpnae mn

  axial axis of the bearing ring 13 under the effect of

  The adjusting nut 14 is applied against it and the clamping screw 15 which is screwed into this nut. As soon as a predetermined angle of rotation of the control shaft 7 has been exceeded, the pin 31a comes, due to the axial displacement of the adjusting ring 29 on the edge of the oblique groove 30a which faces, in a position such that a new pivoting of the control shaft 7 under the effect of a corresponding additional axial displacement of the adjusting ring 29 rotates the latter. During this rotation, a relative displacement of the conical surface 41 of the adjusting ring 29 relative to the annular edge 42 of the adjusting nut 14 takes place, because the bearing ring 13 is supported by its flange on the adjusting nut 14, so that it can not rotate. When the different brake elements are returned to their starting position when the brake shoes are released under the effect of

  spring 24, the adjustment ring 29 drives the adjusting nut

  14 during the pivoting back, under the effect of the pin 31a which fits into its groove 30a. As the clamping screw 15 is prevented from turning by the slide 43 which fits into the groove 44, the clamping screw will be

  unscrewed, during this relative rotation of the adjusting nut

  it glues 14 with respect to the clamping screw 15, in view of the

  compensation for the wear of the brake lining.

  It is obvious in this embodiment that

  that can be used instead of the conical surface

  41 with the annular edge 42, the oblique toothing 34, 35 used

  in the first embodiment according to Figure 1.

  In the third embodiment which is

  6, 7 and 8, the tightening screw 15 screwed into the adjusting nut 14 is applied, by its end

  front, on a piston 121 which maintains the support of

  brake assembly. The guide pin 19 serves to prevent the bearing ring 13 from rotating, passes through a groove 122,

  parallel to the axis, which is formed in the piston 121.

  An annular seal 126, made of elastic plastic material, which is placed between the sliding saddle 1 and the

  tightening screw 15, protects the control mechanism of the in-

  troduction of foreign bodies, dirt and moisture.

  On the rear side, facing away from the oblique raceway 10, the collar 9 is provided an axial bearing 27, through which the control shaft 7 is supported on an annular disk 128, which on a flange 142, which is connected to the sliding saddle 1 by four screws

143.

  The adjusting nut 14 is connected so that it can not

  turn, to a piece of extension 141 by means of a gou-

  pille 124, and is thus in functional engagement with the

adjusting device.

  An adjusting sleeve 144 is permanently screwed onto the extension piece 141, and a locknut 125 prevents it from loosening. For the connection to be absolutely safe, the extension piece 141 has a slot 137, in which

  which is formed by deformation of a cylindrical portion

  protruding from the locknut 125, a serration 138 which appears better in Figure 8. By means of a compression spring 123, the entire adjustment device 144, 141, 124, 14, is applied by the shoulder 17 on the

  bearing ring 13 and thus maintains, without play, the mechanism

  9, 11, 13 on the ball guides 10, 12.

  With the aid of an adjusting nut 139, which is screwed on the control shaft and rotates on the flange 142 by a pressure disc 140, the axial bearing 127 is shown without play.

  As shown in Figure 6, on the end of the

  setting 144, 141, 124, 14 which is turned to oppo-

  of the shoulder 17 is mounted so as to be rotatable,

  a setting ring 129o This adjusting ring 129 com-

  door, as shown in Figure 7 two square studs 131, which fit into the axial grooves 130 of the control shaft 7; the pins 131 having thicknesses smaller than the widths of the axial grooves-130 the difference being equal to the clearance L. Between the locknut 125 and the adjusting ring 129

  a compression spring 133 is provided under the action of

  the adjusting ring 129 is held in place, by its oblique toothing 134 sawtooth on its end face, on a corresponding oblique toothing 135 of the sleeve of re

setting 14.

  The control element which is located near the control lever 8 is protected by a special seal 132, made of elastic plastic material, of the introduction of foreign bodies and

humidity.

  The disc brake just described works

as follows.

  When turning the control shaft 7 by means of

  lever 8, the balls 11 travel on a track on the

  10 or 12 oblique bearing minutes, which leads to

  that the bearing ring 13 moves on the disk of

  6. The ring drives the adjusting nut 14 by means of

  intermediate of the shoulder 17, as well as the clamping screw

  which is screwed into this nut, resulting in

  intermediate piston 121, an application on the brake disc 6, the brake lining 3 fixed on the support 2 brake lining. By virtue of the reaction force, the sliding saddle 1 is displaced axially to the right with respect to the brake disc 6, until 24934 [i41 finally the brake pad holder 2 which is on the half 4 of the saddle comes to apply by its filling

  brake 3 on the brake disc 6.

  During the rotation of the control shaft 7, its collar 9 is supported by means of the axial bearing 127 and

  of the annular disk 128, on the rim 142 of the saddle

  1. When pivoting the control shaft 7, the groove 130 thereof moves relative to the pin 131 of the adjustment shaft 129 by a distance corresponding to

  play L shown in Figure 7. When the wear of the

  When the brake has exceeded a predetermined degree, an even greater rotation angle of the control shaft 7 becomes necessary for the brake application. As a result, the pin 131 eventually comes to apply on the other end

  of the groove 130 and this results in a training of the

  129, so that the latter moves relative to the adjustment sleeve 144. If the rotational movement of the adjusting ring 129 relative to the sleeve

  setting 144 exceeds a distance corresponding to the

  In the case of a tooth of the oblique toothing 134, 135, a tooth of the tooth is broken. During the return movement of the various elements after the end of the braking process, the control shaft 7 drives the pin 131 of the adjusting ring, which drives the adjustment sleeve 144 via the oblique toothing 134, 135 then in take. As the adjustment sleeve 144 is connected to the workpiece

  extension 141 so that it can not turn, that

  ci, and thus also the adjusting nut 14 rotate at the same angle. This has the consequence that the clamping screw 15 is unscrewed from the adjusting nut 14, in the direction of the brake disc 6, to a degree corresponding to the wear of the brake lining. In this way, it is planned at a

  compensation of the wear of the brake lining, by

automatic ge.

  The process of loosening that is necessary when changing the brake lining and a new starting setting, is very simple. The special seal 132 is first removed, and the oblique teeth 134 and 135 are then

- 14 - 2493441

  separated. This is done by sliding the adjusting ring 129 against the compression spring 133, by hand or with the aid of a suitable tool. It is then possible, by applying a wrench on the hexagonal surface of the locknut 125, to bring the clamping screw 15 and the piston 121 into their starting position via the adjustment device! A44 1A1e 124 14,

  In the fourth embodiment, which is repre-

  as shown in FIGS. 9 and 10, adjusting nut 14 is also

  connected in such a way that it can not be

  141. On this piece of equipment 14tl is monged, so as to turn round, a ring adjustment 229, which is based on

  the adjusting nut 14 via a wave spring 233.

  The bag of set. 229 has a groove axia7 230 in the-

  that it is built a stud 231, which part radiates towards the in-

  As shown in FIG. 10, the stud 231 has a smaller diameter, the axial groove width 230, the difference corresponding to the clearance L of the brake. An adjustment sleeve 244 is fixed on the extension piece 141 with the interposition of a tolerance ring

  245, and a safety ring 246 prevents it from loosening.

  An oblique toothing 234 of the adjusting ring 229, sawtooth on its front side, is held in engagement, under the action of the corrugated spring 233, with an oblique toothing 235 arranged

  on the adjacent front side of the adjustment sleeve 244.

  On the anterior end of the extension piece

  141 is screwed against a nut 125. A helical spring 123 is supported on a disc 248 applied to the nut 125 and on a

  narrowing 249 of the control shaft 7.

  The entire adjustment device 244, 229, 141 is applied to the bearing ring 13, with the shoulder 17 of

  the adjusting nut 14, by this compression spring 123, and the

  9, 11, 13 thus maintained without play on the

guides of balls 10 and 12.

  In the front end of the control shaft 7,

24934- 1

* Screws a 232 wear compensation screw, to protect the

  device for adjusting the introduction of dirt or water.

  The sliding saddle disc brake which is

  felt in Figures 9 and 10 works in principle as

  the third embodiment described above.

  When the control shaft 7 is rotated through

  8, its peg 231 moves relative to the groove 230 of the adjusting ring 229 by a distance corresponding to the clearance L shown in FIG.

  the wear of the brake lining has exceeded a pre-

  determined, an even greater rotation angle of the control shaft 7 is necessary for the clamping of the brake. As a result, the pin 231 ends up being applied to the other end of the groove 230 and the adjusting ring

  229 ends up being trained, so that this last

  the ring moves with respect to the adjusting sleeve

  244. When the rotation of the adjusting ring 229

  port at adjustment sleeve 244 exceeds the width of a tooth

  oblique toothing 234, 235, a tooth of the set of teeth

  that is found jumped. During the return movement of these elements after the end of the braking process, the control shaft 7 drives, with the pin 231, the adjusting ring

  229, which drives the adjustment sleeve 244 through the

  intermediate oblique toothings 234 and 235 then in mesh.

  As the adjusting sleeve 244 is frictionally connected to the extension piece 141 through the tolerance ring 245, this extension piece, and therefore also the adjusting nut 14, rotates at the same angle. This has the consequence that the clamping screw 15 is unscrewed from the adjusting nut 14, in the direction of the brake disk 6, by a distance corresponding to the wear of the brake pad.

  brake. In this way, the wear of the lining is

thought automatically.

  The loosening process, which is necessary during the

  change of the brake lining and in a new

  glage of departure, is infinitely simple. We start with

  lift the wear compensation screw 232, and apply

  following a socket wrench on the lock nut 125, to rotate the extension piece 141 and the adjusting nut 14 with it. The clamping screw 15 is thus, in the direction of rotation of the locknut 125, unscrewed from the adjusting nut 14 or screwed into it. The adjustment sleeve 244 itself is engaged by means of the oblique toothing 234 and 235 with the adjusting ring 229 which is rotatably connected via the pin 231. , at the control shaft 7. There is

  As a result, the adjustment sleeve 244 can not rotate independently.

  from the control shaft 7. But because of this, the adjustment process is not prevented, because the

  static friction of the tolerance ring 245 can easily

  to be overcome by the moment of rotation exercised with

  the socket wrench on the lock nut 125.

24934i4

Claims (23)

  1. A mechanically actuated disc brake having a sliding saddle mounted transversely to the brake disc and covering the brake disc each of the two halves of the saddle carrying a brake lining carrier with its a control shaft being rotatably mounted in one   half of the saddle and have at the end   in the form of a box, a radial projecting collar-   which is equipped on one of its sides with   oblique bearings intended to receive balls which   respond to oblique bearing paths provided on   a bearing ring and which serve to transform the movement   rotation of the control shaft in an axial displacement of a clamping screw on one of the brake lining supports, and comprising a play-compensating device which comprises a control ring coaxial with the screw of tightening, placed with the control shaft in relation   such as when the control shaft has   angle greater than that which corresponds to a determined wear of the lining and that an adjusting nut   this tree turned at the same time returning to its posi-   starting during the release of the brake, this ring unscrews the clamping screw and is thus interposed in the flow of forces transmitted from the control shaft to the clamping screw,   Characterized in that the control shaft (7)   on the sliding saddle (1) via an axial bearing (27; 127) to prevent axial movement of the side of the collar (9) facing the oblique raceways (10, 12), in that that the bearing ring (13) can move axially with respect to the brake saddle (1), but can not turn and applies the adjusting nut (14)   in the form of a sleeve, and that the adjusting ring   ge (29; 129; 229) is rotatably mounted on the adjusting nut (14) and is coupled to a control device consisting of a groove (30; 30a; 130; 230) and a pin (31; 31a; 131; 231) embedded in the groove which causes the adjusting ring (29; 129; 229) to rotate when the control shaft (7) rotates or the ring   bearing (13) moves axially as a result of this rotation.   tation. Disc brake according to Claim 1, characterized   in that the groove (30; 130; 230) of the coupling device   mande is directed parallel to the tree of the com-   Means (7) and is provided either in the coortland sleeve or in the adjusting ring (2'-; 229), and in that the pin (31; 131; 231) is attached either to the adjusting ring (129 ) either on the control shaft (7).   Disc brake according to claim 1, characterized   in that the groove (30a) of the control device is di-   seated obliquely to the axis of the drive shaft (7) and is arranged either in the saddle (1) t or in the adjusting ring (29), and in that the pin (31a) is fixed either on the adjusting ring (29) or on the sliding saddle (1).   4. Disc brake according to claim 1, characterized in that the adjusting ring (29) is applied to an annular edge (42) of the adjusting nut (14) by means of a surface   of substantially conical shape (41) under the action of a res-   compression fate (33) acting axially on it.   5. Disc brake according to claim 1, characterized in that the adjusting ring (29) is applied under the action of a compression spring (33) acting axially on it by an oblique toothing (34). sawtooth on his   front side, on a frontal surface, having a den-   correspondingly (35) of the adjusting nut (14).   Disc brake according to claim 1, characterized in that the bearing ring (13) bears against a radially projecting shoulder (17) of the adjusting nut (14) and in that is intended to prevent him from turning,   a guide groove (18) parallel to the axis and in the   which is fitted a guide pin (19) crossing radially the saddle (1).   Disc brake according to claim 1, characterized   in that the tenon (31a) fits into the oblong groove   that (30a) protrudes from the outer end of the guide pin (19) passing through the guide groove (18) of the bearing ring (13).   8. Disc brake according to claim 6 or 7, characterized in that the guide pin (19) is cylindrical and   has flats (36) in the region of the guide groove age (18).   Disc brake according to any one of the claims   6 to 8, characterized in that the guide pin (19) is provided at its rear end with a radial shoulder   (37) which determines, in connection with a corresponding rotation,   associated hole in the sliding saddle,   how far the pin (31) protrudes from the hole.   Disc brake according to claim 9, characterized in that a hole section receiving the guide pin   (19) is connected to an outer section, provided with a thread   ge, to receive one of the screws (38) with hexagon socket which fix the guide pin.   11. Disc brake according to claims 8 and 10,   characterized in that it is intended for the alignment of   flats (36) of the guide post (19) with respect to   in the region of the rotation of the hole in the sliding saddle, a pin (39), to which is associated a slot (40) in the area of   the radial shoulder (37) of the guide pin (19).   Disc brake according to any one of the claims   1 to 11, characterized in that the clamping screw (15) is provided with a ruler (43) which extends radially from it and which fits into a groove (44) of the sliding saddle (1) Disc brake according to claim 1, characterized in that the adjusting device (144, 141, 24, 14) is   disposed outside the sliding saddle (1).   Disc brake according to Claim 13, characterized in that the adjusting nut (14) is connected in such a way that   to be able to turn, to an extension piece (141) which   coaxially lays down the control shaft (7) and which is connected, so as to be rotatable, on its end   free from the control shaft, to a setting sleeve ge (144).   15. Disc brake according to claim 14, characterized in that the adjusting ring (129> is included, under   the action of a compression spring (133) acting axially   on it, by an oblique toothing (134), in teeth of   sawing on its frontal side, on a frontal surface, presented   both a corresponding toothing (135) of the adjusting sleeve 144).   Disk brake according to Claim 15, characterized in that the free end of the extension piece (141) is provided with an external thread on which the adjusting sleeve (144) and a counter nut are screwed. (125), the compression spring (133> thus relying on   the adjusting ring (129) and the locknut (125).   17. Disc brake according to claim 16, characterized in that the extension piece (141) is provided, in the frontal surface of its free end, with a slot (137) in which a locking deformation ( 138) formed on a projecting cylindrical portion of the locknut (125).   Disc brake according to any of the claims   14 to 16, characterized in that on the control shaft (7) is fitted a seal (132) in the form of   cup, which surrounds the free end of the piece of pro- long (141).   Disc brake according to Claim 1, characterized in that the adjusting nut (14) is connected in such a way that   to be able to turn, to an extension piece (141) which   coaxially accommodates the control shaft (7), and that an adjusting sleeve (244) coupled to the adjusting ring (229) is connected to the extension piece (141) by a friction coupling (245).   Disc brake according to Claim 19, characterized in that the adjusting sleeve (244) is attached to the workpiece   extension (141) with interposition of a ring of management (245).   Disc brake according to Claim 20, characterized in that the adjusting ring (229) is applied under   the action of a compression spring (233) which acts axially   on it, by an oblique toothing <234), sawtooth on its front side, on a front surface, presenting a corresponding oblique toothing (235) of the sleeve of setting (244).   22. Disk brake according to claim 21, characterized in that the free end of the extension piece (141) is provided with an external thread on which is screwed a locknut (125).   Disc brake according to any one of the claims   19 to 22, characterized in that a wear compensation screw (232) is screwed into the free end of the control shaft 7.