SPREADER UNIT FOR A DRUM BRAKE, COMPRISING WEAR TRAVEL ADJUSTMENT, AND THE DRUM BRAKE

Abstract

An improved electromechanically drivable spreader unit having an integrated adjustment apparatus for a drum brake, in which the linear motion of brake shoe holders is produced by two ball-ramp devices, wherein a first ball-ramp device includes a first actuation piston arranged for rotation about the axis and a second ball-ramp device includes a second actuation piston arranged for rotation about the axis, and wherein an adjustment apparatus for compensating an actuation travel that increases as a result of wear on the friction linings is arranged in an axially centered position within the housing and substantially between the actuation pistons.

Claims

1. An electromechanically drivable spreader unit for a drum brake comprising: a housing and two first and second brake shoe holders, which are arranged in a manner secured against rotation in relation to the housing and which can be actuated linearly along an axis, respectively away from one another in a spreading direction and toward one another in a release direction, and act respectively on a first and second brake shoe, each of which is provided with a brake lining, wherein the linear motion of the brake shoe holders is produced by two ball-ramp devices, wherein a first ball-ramp device comprises a first actuation piston arranged for rotation about the axis and a second ball-ramp device comprises a second actuation piston arranged for rotation about the axis, and wherein an adjustment apparatus for compensating an actuation travel that increases as a result of wear on the friction linings is arranged in an axially centered position and substantially between the actuation pistons within the housing.

2. The spreader unit as claimed in claim 1, wherein the actuation pistons are arranged in an axially floating manner in a driving sleeve and are secured against the latter against rotation, and wherein the driving sleeve is provided with a torque by an electromechanical drive unit and is mounted in the housing for rotation about the axis.

3. The spreader unit as claimed in claim 1, wherein the adjustment apparatus comprises an adjustment piston, which is in the same force transmission path as the first actuation piston, and a latching sleeve, which is in engagement with the adjustment piston via axial toothed rings, and wherein the latching sleeve is secured against rotation relative to the second brake shoe holder, can be moved axially to a limited extent relative to the second actuation piston and is arranged under elastic preload against the adjustment piston.

4. The spreader unit as claimed in claim 3, wherein the toothed rings are formed in such a way, in a mutually corresponding manner, on the same circumferential circle by ramps oriented and inclined in a circumferential direction that rotation thereof relative to one another is blocked in one circumferential direction and brings about an axially directed force in the opposite circumferential direction.

5. The spreader unit as claimed in claim 3, wherein the second ball-ramp device comprises a spreader piston arranged in a manner secured against rotation relative to the second brake shoe holder, and wherein the spreader piston has a stem projecting in the direction of the first actuation piston, and the latching sleeve is arranged in a manner secured against rotation and guided in a manner which allows axial movement on the stem.

6. The spreader unit as claimed in claim 3, thot w the latching sleeve is pressed against the adjustment piston by a compression spring, wherein the compression spring is supported on the second actuation piston.

7. The spreader unit as claimed in claim 3, wherein the first actuation piston and the adjustment piston are connected to one another by a screw threaded joint coaxial with the axis.

8. The spreader unit as claimed in claim 1, wherein each brake shoe holder is axially movable in the direction of a respectively associated ball-ramp device, in the process compressing a spring element arranged under preload therebetween.

9. The spreader unit as claimed in claim 1, wherein the spreader unit is mounted in the drum brake so as to float along the axis.

10. A drum brake comprising at least one spreader unit as claimed in claim 1.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Further features, advantages, and potential applications of an aspect of the invention are derived from the following description of an exemplary embodiment according to the invention. In this connection:

[0020] FIG. 1 shows a highly simplified sectional view into a drum brake of simplex design with a spreader unit according to an aspect of the invention.

[0021] FIG. 2 shows an embodiment according to the invention of the spreader unit in axial section.

[0022] FIG. 3 shows the spreader unit according to FIG. 2 in a three-dimensional exploded illustration.

[0023] FIG. 4 shows a partially disassembled spreader unit according to FIG. 2 in axial section.

[0024] FIG. 5 shows a three-dimensional view of the illustration according to FIG. 4.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0025] Because the fundamental manner of operation both of a drum brake and of a ball-ramp device is sufficiently well known, only those functional characteristics which are essential to an aspect of the invention will be explored below.

FIG. 1

[0026] FIG. 1 shows, by way of example and in a highly simplified form, a drum brake of the type in question of simplex design. Other known designs of drum brake can likewise be adapted within an aspect of the invention, however.

[0027] Two substantially circular-arc-shaped brake shoes 4, 4′, supported pivotably at the first end 13, 13′ thereof, are each spread apart at the second end 12, 12′ thereof by a spreader unit 2 and, in the process, are pressed against the radially inner wall 7 of a pot-shaped brake drum 6. The brake drum 6 is connected to a vehicle wheel (not shown) and rotates together with the latter relative to the brake shoes 4, 4′. During this process, the brake linings 5, 5′ attached to the brake shoes 4, 4′ rub against the inner wall 7. Due to the wear of the brake linings 5, 5′, the spreading travel required for a braking process increases continuously up to a defined wear limit.

[0028] In order to compensate any asymmetric, nonuniform contact between the linings 5, 5′ and the brake drum 6, the spreader unit 2 is preferably arranged in such a way as to be mounted to float in the drum brake, preferably along the central axis A thereof.

FIG. 2

[0029] FIG. 2 shows an embodiment according to the invention of the spreader unit 2 in an unactuated initial state in axial section. The spreader unit 2 has two ball-ramp devices 3, 3′, which act on the brake shoes 4, 4′ via the brake shoe holders 31, 31′. For this purpose, each brake shoe holder 31, 31′ has a transverse slot 36, 36′, in each of which a flat end 12, 12′ of a brake shoe 4, 4′ is arranged. The spreader unit 2 furthermore has a substantially tubular housing 14 equipped with a mounting flange. The driving of the spreader unit 2 is performed by an electric-motor drive unit 8 indicated in FIG. 1 via the external toothing 10 of a driving sleeve 9, which is thereby rotated about the axis A and is supported in the housing 14 via rolling bearings 15, 15′ and is fixed axially by retaining elements 16, 16′. Because the drum brake 1 according to an aspect of the invention is provided as a service brake, all the braking processes and not just a static, constant application of force during parking, for instance, are initiated via the driving sleeve 9. In the embodiment shown, the rolling bearings 15, 15′ are designed as needle bearings, but other types of rolling bearing are likewise permissible within an aspect of the invention.

[0030] The braking process is performed via the ball-ramp devices 3, 3′ on the brake shoe holders 31, 31′ and the brake shoes 4, 4′ in engagement therewith.

[0031] Each ball-ramp device 3, 3′ essentially comprises a spreader piston 22, 23, an actuation piston 17, 18 rotatable about the axis A relative to the spreader piston 24, 25, and a multiplicity of balls 34. On their respectively facing ends, the first actuation piston 17 and the first spreader piston 22, and the second actuation piston 18 and the second spreader piston 23, each have an equal number of depressions 32, 33 on the same circumferential circle, said depressions being arranged in a manner distributed regularly in the circumferential direction. The depressions 32 in the actuation pistons 17, 18 are each designed to flatten out gradually in a first circumferential direction, the depressions 33 in the spreader pistons 22, 23 correspond to the depressions 22 but are flattened out in a second, opposite circumferential direction. A ball 34 is arranged between each depression 32 and 33. By virtue of the rotation of the actuation pistons 17, 18 relative to the spreader piston 22, 23 in an actuating direction, the balls 34 roll into the flattened-out regions of the depressions 32, 33 and push the piston pairs apart (and vice versa).

[0032] The two spreader pistons 22, 23 are secured against rotation in relation to the housing 14 and can thus only be moved linearly along the axis A. In the embodiment shown, the security against rotation is ensured by the support of the respective brake shoe holder 31, 31′ on the brake shoe 4, 4′ via the transverse slot 36, 36′. In this case, each brake shoe holder 31, 31′ is connected in a manner secured against rotation to the respective associated spreader piston 22, 23 via an outer sleeve 35, 35′ bent inward at the edges. In this case, each spreader piston 22, 23 is arranged spaced apart axially from the associated brake shoe holder 31, 31′ within the outer sleeve 35, 35′, with in each case a spring element 37, 37′ preloaded therebetween.

[0033] As a result, a limited linear motion in the axial direction is made possible and this ensures that, as the drum shrinks, the increase in clamping force is limited by the compression of the spring elements 37 in order to exclude damage to the brake. With the abovementioned construction, a robust, easy-to-handle, pre-assemblable spreader piston unit 24, 25 is also created, said unit in each case essentially comprising a spreader piston 22, 23, a brake shoe holder 31, 31′, a spring element 37, 37′ and an outer sleeve 35, 35′.

[0034] Further solutions for providing security against rotation, which are not shown here, for spreader pistons 22, 23, e.g. by means of various axial guides relative to the housing 14, are likewise conceivable within an aspect of the invention.

[0035] The transmission of rotary motion required for the ball-ramp devices 3, 3′ is performed by means of a first actuation piston 17 and a second actuation piston 18.

[0036] For the purpose of uniform contact between the brake linings 5, 5′ and the inner wall 7, the two actuation pistons 17, 18 are arranged in the driving sleeve 9 in an axially floating manner and in a manner secured against rotation by means of axial guide 11. In the embodiment illustrated, the axial guide is formed by means of an axial toothing geometry, in particular axial splines. Further embodiments, e.g. projections engaging in axial grooves and the like are likewise permissible within an aspect of the invention.

[0037] An adjustment apparatus 26 essentially comprises an adjustment piston 19, which is in the same force transmission path as the first actuation piston 17, and a latching sleeve 27, which is in engagement with the adjustment piston 19 and is arranged in a manner secured against rotation relative to the second spreader piston 28 but in a manner which allows axial movement to a limited extent and under elastic preload against the adjustment piston.

[0038] A separate adjustment piston 19 is screwed into a threaded hole 20 in the first actuation piston 17 as far as a stop position by means of a threaded section 21 and thus lies in the force transmission path between the first actuation piston 17 and the second actuation piston 18. On its end facing the second actuation piston 18, the adjustment piston 19 has an axially projecting annular first toothed ring 38 having a plurality of tooth-shaped ramps 40 or notches sloping in one circumferential direction.

[0039] The latching sleeve 27 is arranged in a manner substantially integrated into the second actuation piston 18. It has an axially projecting annular second toothed ring 39, which corresponds to the first toothed ring 38 and which likewise consists of a plurality of tooth-shaped ramps 41 or notches sloping in an opposite circumferential direction.

[0040] The latching sleeve 27 is mounted in a manner which allows axial movement and in a manner secured against rotation in relation to the housing 14 on a stem 28 of the second spreader piston 23 by means of a central hole. In the embodiment shown, a transverse pin 29 is provided in the stem 28 to prevent rotation, the latching sleeve 27 being supported on said pin in both circumferential directions by means of an axially projecting slotted collar 42.

[0041] The latching sleeve 27 is pressed continuously with a slight force onto the toothed ring 38 of the adjustment piston 19 by a compression spring 30 supported on the second actuation piston 18. A sliding disk 43 reduces the friction and the rotation of the compression spring 30 when the second actuation piston 18 is rotated.

[0042] In the embodiment shown, the compression spring 30 is designed as a wave spring. Further embodiments, e.g. a spiral spring or a Belleville spring assembly, are likewise permissible within an aspect of the invention.

[0043] When the two actuation pistons 17 and 18 are driven by the driving sleeve 9, the adjustment piston 19 is rotated relative to the latching sleeve 27, which is immovable in the circumferential direction. During this process, the ramps 40 of the adjustment piston 19 run up onto the ramps 41 of the latching sleeve 27 during each actuation or braking operation and push them slightly into the second actuation piston 18, counter to the spring action of the compression spring 30. With increasing wear of the brake linings 5, 5′, the required stroke and thus the angle of rotation of the driving sleeve 9 and of the adjustment piston 19 coupled thereto increases. As soon as the angle exceeds the circumferential length of a ramp 38 or 41, the axial toothing between the latching sleeve 27 and the adjustment piston 19 jumps into the next notch. If the brake is then released after a braking process, the first actuation piston 17 rotates back into the unactuated initial position together with the driving sleeve 9. However, the adjustment piston 19 is hindered from rotating back by the rotationally secured latching sleeve 27 and, as a result, is unscrewed by the corresponding amount from the first actuation piston 17. Thus, an adjustment process takes place fully automatically in steps under travel control during the release process of the drum brake 1.

[0044] FIGS. 3 to 5 show the spreader unit 2 according to an aspect of the invention shown in FIG. 2 in further illustrations and views and serve to clarify the above presented facts and construction.

LIST OF REFERENCE SIGNS

[0045] 1 Drum brake [0046] 2 Spreader unit [0047] 3 Ball-ramp device [0048] 4 Brake shoe [0049] 5 Brake lining [0050] 6 Brake drum [0051] 7 Inner wall [0052] 8 Drive unit [0053] 9 Driving sleeve [0054] 10 External toothing [0055] 11 Axial guide (axial toothing, splines) [0056] 12 End [0057] 13 End [0058] 14 Housing [0059] 15 Rolling bearing (needle bearing) [0060] 16 Retaining element [0061] 17 Actuation piston [0062] 18 Actuation piston [0063] 19 Adjustment piston [0064] 20 Threaded hole [0065] 21 Threaded section [0066] 22 Spreader piston [0067] 23 Spreader piston [0068] 24 Spreader piston unit [0069] 25 Spreader piston unit [0070] 26 Adjustment apparatus [0071] 27 Latching sleeve [0072] 28 Stem [0073] 29 Transverse pin [0074] 30 Compression spring [0075] 31 Brake shoe holder [0076] 32 Depression [0077] 33 Depression [0078] 34 Ball [0079] 35 Outer sleeve [0080] 36 Transverse slot [0081] 37 Spring element [0082] 38 Toothed ring [0083] 39 Toothed ring [0084] 40 Ramp [0085] 41 Ramp [0086] 42 Collar [0087] 43 Sliding disk [0088] A Axis