Disk Brake for a Utility Vehicle

Abstract

A disk brake with lower cost and improved maintainability is provided. The brake caliper includes at least one actuating device for actuating the disc brake using a moveably guided bridge. The bridge has at least one threaded hole into which an actuating spindle is displaceably located. A brake disk end of the actuating spindle penetrates a caliper closing plate facing the brake disk. The positioning spindle carries a rotatably-mounted pressure piece which presses a brake pad against the brake disc. The opening is sealed by a bellows retained on the brake caliper on one side and on the pressure piece on the other side. A securing ring non-rotatably located on the actuating spindle and rotatably connected to the thrust piece interacts with the bellows during brake application and/or release to maintain a desired air gap between the brake disk and brake pad.

Claims

1. A disk brake for a utility vehicle, comprising: a brake caliper configured to straddle a disk brake, the brake caliper including at least one application device arranged in a region of the brake caliper configured to receive the at least one brake application device, a guided bridge configured to displace the at least one application device in a direction toward the brake disk, an actuating spindle configured to be supported in a bore of the guided bridge, a closure plate configured to close the region of the brake caliper configured to receive the at least one brake application device, the closure plate having an aperture through which the actuating spindle extends in the direction toward the brake disk, a thrust piece axially and rotatably supported on the actuating spindle between the actuating spindle and a brake pad configured to be pressed against the brake disk, a readjustment device configured to adjust an air gap between the brake disk and the brake pad, the readjustment device being operatively connected to the actuating spindle, a bellows configured to seal off a passage region of the actuating spindle at the closure plate aperture, the bellows having an outer circumferential portion configured to be connected to closure plate and an inner circumferential portion configured to be connected to the thrust piece, and a securing ring configured to be located in an non-rotating manner on the actuating spindle and on the thrust piece in an axially secured and relatively rotatable manner.

2. The disk brake as claimed in claim 1, wherein the securing ring is held in positively locking fashion on the actuating spindle.

3. The disk brake as claimed in claim 2, wherein the securing ring has spring arms configured to lie in axial grooves of the actuating spindle.

4. The disk brake as claimed in claim 3, wherein the securing ring is composed of a resilient material, preferably spring steel.

5. The disk brake as claimed in claim 4, wherein the resilient material is spring steel.

6. The disk brake as claimed in claim 5, wherein the securing ring has a slot configured to allow the securing ring to be installed in a radial direction onto the actuating spindle.

7. The disk brake as claimed in claim 6, wherein the thrust piece has an opening configured to receive a thickened head of the actuating spindle, and the securing ring has radially oriented tabs configured to engage into a circumferential groove on a wall of the thrust piece opening.

8. The disk brake as claimed in claim 7, wherein a diameter of the securing ring prior to installation on the actuating spindle is smaller than a diameter of the thickened head of the actuating spindle.

9. The disk brake as claimed in claim 8, wherein the securing ring has axially oriented lugs configured to lie in recesses of a pot-shaped secondary seal, and the pot-shaped secondary seal outer circumferential portion is pressed into the opening of the closure plate and the inner circumferential portion is fastened to the guided bridge.

10. The disk brake as claimed in claim 9, wherein the bellows has a plurality of recesses arranged circumferentially around a radially inner surface of the inner circumferential portion.

11. The disk brake as claimed in claim 10, wherein a circumferential length of each of the plurality the recesses is greater than a circumferential length of each a plurality of webs between adjacent ones of the plurality of recesses.

12. The disk brake as claimed in claim 11, wherein the securing ring has a polygonal circumferential contour.

13. The disk brake as claimed in claim 12, wherein the spring arms each have a limb angled radially inward which is configured to lay in a corresponding one of the actuating spindle axial grooves.

14. The disk brake as claimed in claim 13, wherein the axial grooves uniformly spaced about the circumference of the actuating spindle.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0024] FIG. 1 shows a disk brake in accordance with the present invention in a partially sectional plan view.

[0025] FIG. 2 shows an assembly of the FIG. 1 disk brake in a partially exploded illustration.

[0026] FIG. 3 shows the assembly as per FIG. 2 in an operating position, in a perspective view.

[0027] FIG. 4 shows the assembly as per FIG. 3 in a sectional plan view.

[0028] FIGS. 5A-5C show a detail of the FIG. 1 disk brake in multiple different views.

[0029] FIGS. 6A-6B shows a further detail of the FIG. 1 disk brake in multiple different views.

DETAILED DESCRIPTION OF THE DRAWINGS

[0030] FIG. 1 illustrates a disk brake for a utility vehicle, having a brake caliper 1 which engages over a vehicle-side brake disk 2 and which is mounted on a brake carrier 4 by means of guide rods 14 so as to be axially displaceable relative to the brake disk 2.

[0031] In the brake caliper 1, there is arranged an application device 5, having a brake lever 7 which acts on a bridge 6 during a braking operation. In the example, two actuating spindles 10 which are arranged parallel to and spaced apart from one another are held in said bridge. The actuating spindles bear in each case one thrust piece 11 facing toward the brake disk 2. During a braking operation, the thrust pieces 11 can be pressed against an associated brake pad 3 which is pressed against the brake disk 2. An oppositely situated, reaction-side brake pad 3 is correspondingly pressed against the brake disk 2 as the brake caliper is axially displaced in response to the actuation of application device 5.

[0032] For the compensation of a changing air gap, that is to say the distance between the brake pad 3 and the brake disk 2 during actuation of the brake, the actuating spindles 10 are rotatable in the direction of the brake disk 2 by a readjustment device 8. For this purpose, the actuating spindles 10 are equipped with an external thread which engages into an internal thread of the bridge 6.

[0033] For the synchronization of the readjustment, a traction mechanism drive is provided, having a traction mechanism 9, for example in the form of a chain.

[0034] For the resetting of the bridge 6 after a release of the brake, a compression spring 13 is provided which is supported at one side on the bridge 6 and at the other side on a closure plate 12. The closure plate closes off a receiving space which receives the application device 5 of the brake caliper 1, on the side facing toward the brake disk 2. The closure plate is in this case fixedly connected to the brake caliper 1, for example by screw connection.

[0035] FIGS. 2 and 3 illustrate a part of the disk brake which, as a preassembled structural unit, is composed of the bridge 6, the traction mechanism drive 9, the actuating spindles 10 and the thrust pieces 11 and the closure plate 12. The completed unit is inserted into the brake caliper 1.

[0036] According to the invention, a securing ring 15 is arranged on the respective actuating spindle 10 in a manner secured against relative rotation. The associated thrust piece 11 is held on the respective actuating spindle 10 in an axially secured and relatively rotatable manner.

[0037] For the securing to the actuating spindle 10 in a manner secured against relative rotation, the securing ring 15 has spring arms 20 which engage into axial grooves 19 of the actuating spindles 10.

[0038] FIG. 2 shows a pre-assembled position of the thrust pieces 11 with respect to the actuating spindles 10, whereas FIGS. 3 and 4 each show the assembled position of the thrust pieces 11.

[0039] In FIG. 4, it can moreover be seen that the passage region of the actuating spindles 10 through the closure plate 12 is sealed off in each case by means of a bellows 16, in this case a corrugated bellows, which is held at one side on the thrust piece 11 and at the other side on the closure plate 12.

[0040] For the latter fastening, a secondary seal 17 is provided in the manner of a pot with a ring as a dimensionally stable component and which is pressed into the passage opening of the closure plate 12 and on which the bellows 16 is held, whereas the secondary seal 17 is fastened at the other side to the bridge 6.

[0041] The securing ring 15 is shown as a detail in FIG. 5, wherein FIG. 5A shows a perspective view, FIG. 5B shows a plan view, and FIG. 5C shows a side view.

[0042] It can be seen in particular in FIG. 5B that the securing ring 15 has a polygonal contour, the corners of which bear against the wall of an opening of the thrust piece 11 which receives a thickened head of the actuating spindle 10. The securing ring 15, which is formed from spring steel, has a slot extending axially all the way through, such that it can be easily spread open.

[0043] In this way, the securing ring 15 can be pushed over the thickened head of the actuating spindle 10 until it has been brought into an end position behind the thickened head. The spring arms 20 then lie with inwardly angled limbs in the axial grooves 19 of the actuating spindle 10. In the example, three axial grooves 19 and spring arms 20 are provided, which are arranged at equal angular intervals with respect to one another.

[0044] It can furthermore be clearly seen in FIG. 5 that the securing ring 15 has radially outwardly directed tabs 21 which, for the axial securing of the thrust piece 11, engage into an encircling groove 23 of the opening of the thrust piece 11 which receives the thickened head of the actuating spindle 10.

[0045] On the side averted from the tabs 21, lugs 22 are integrally formed on the securing ring 15. The lugs 22 engage into cutouts 18 of the ring of the secondary seal 17 in the event of a backward rotation of the actuating spindle 10 (FIG. 4).

[0046] FIG. 6 illustrates the secondary seal 17 as a detail, specifically in a plan view in FIG. 6A and in a sectional side view in FIG. 6B.

[0047] Here, webs 24 formed between the recesses 18 are designed such that their length in the direction of rotation, converted by the transmission ratio of the thread of the actuating spindle 10, is jumped over in the case of an axial backward-rotation travel of 0.1 mm during the backward rotation of the actuating spindle 10. By contrast, the recesses 18 are dimensioned in the same direction such that an axial backward-rotation travel of 0.4 mm is covered.

[0048] It must be ensured that the securing ring 15 is not axially braced with the secondary seal 17. This is achieved by virtue of the fact that the spring arms lying in the axial grooves 19 are designed to be resilient in an axial direction, such that the 0.1 mm axial backward-rotation travel required for the jump-over of a web 24 on the secondary seal 17 is absorbed by the spring action.

[0049] During the further backward rotation of the actuating spindle 10, the flanks of the lugs 22 of the securing ring 15 come into contact with the flanks of the webs 24 of the secondary seal 17, and the acting torque of for example approximately 35 Nm is absorbed only in the circumferential direction. The interference fit of the secondary seal 17 with respect to the bridge 6 is configured such that said torque can be transmitted.

[0050] Although the contact area between the securing ring 15 and the secondary seal 17 is very small, local plasticization occurs on the secondary seal 17, but this does not constitute a problem because, firstly, a further jump-over of a web 24 is ensured by the available axial backward-rotation travel, and the function of the backward rotation is normally required only 10 times over the service life of the brake.

[0051] The foregoing disclosure has been set forth merely to illustrate the invention and is not intended to be limiting. Since modifications of the disclosed embodiments incorporating the spirit and substance of the invention may occur to persons skilled in the art, the invention should be construed to include everything within the scope of the appended claims and equivalents thereof.

LIST OF REFERENCE DESIGNATIONS

[0052] 1 Brake caliper [0053] 2 Brake disk [0054] 3 Brake pad [0055] 4 Brake carrier [0056] 5 Application device

[0057] 6 Bridge [0058] 7 Brake lever [0059] 8 Readjustment device [0060] 9 Traction mechanism [0061] 10 Actuating spindle [0062] 11 Thrust piece [0063] 12 Closure plate [0064] 13 Compression spring [0065] 14 Guide rod [0066] 15 Securing ring [0067] 16 Bellows [0068] 17 Secondary seal [0069] 18 Recess [0070] 19 Axial groove [0071] 20 Spring arm [0072] 21 Tab [0073] 22 Lug [0074] 23 Groove [0075] 24 Web