DRUM BRAKE

Abstract

For controlling electromechanically actuatable brakes of servo type construction, it is necessary to detect the forces acting on the abutment of the brake shoes. The abutment is therefore formed from a massive material which deforms under load, wherein measurement devices are provided which detect this deformation. The shape of the abutment is selected in such a way that the abutment has measurement gaps, the size of which changes when the abutment is loaded. The size of the measurement gaps can be sensed by means of Hall sensors or AMR sensors, for example.

Claims

1-10. (canceled)

11. A drum brake of servo type construction comprising: a brake drum; two brake shoes, which can be applied to the brake drum, each having a pressure end and a supporting end; a spreader device between the pressure ends of the brake shoes, which is mounted to float relative to the carrier plate and is supported in force introduction points at the pressure ends to introduce force into the pressure ends; a ram located between the supporting ends, which is mounted to float relative to the carrier plate and is supported on the supporting ends in order to transmit force; a pressure head at the pressure end on each brake shoe adjacent to the force introduction point, wherein the pressure heads can be supported on an abutment arranged therebetween and connected to the carrier plate, wherein the abutment is deformed elastically under load; and at least one sensor which detects deformation of the abutment that arises under load to enable the braking torque produced in the drum brake to be determined with the sensor signal.

12. The drum brake as claimed in claim 11, wherein the abutment is formed by a base, which ends via a web at a pedestal connected to the carrier plate, wherein the pressure heads rest against the opposite edges of the base.

13. The drum brake as claimed in claim 11, wherein the base is connected to the pedestal via a central web, wherein the mutually facing edges of the base and the pedestal extend parallel to one another and enclose a measurement gap between them.

14. The drum brake as claimed in claim 12, wherein the abutment has a U-shape with a base and two arms, which projects from the base, wherein the pressure heads are supported on the outer edges thereof, and the at least one sensor can detect the slope of the arms, which changes under load.

15. The drum brake as claimed in claim 11, wherein the base is carried by a central web starting from a pedestal secured on the carrier plate and adjoining the inner edge of the base, wherein the arms are oriented toward the carrier plate.

16. The drum brake as claimed in claim 15, wherein pins projecting laterally from the central web reach the inner edges of the arms, forming a measurement gap.

17. The drum brake as claimed in claim 15, wherein the base and the pedestal are connected to one another via two struts situated at the edges to form a frame, wherein at least one pin starting from the pedestal extends to the inner edge of the base to form a measurement gap.

18. The drum brake as claimed in claim 15, wherein the pedestal, the webs, and the base form an integral component.

19. The drum brake as claimed in claim 11, wherein at least one strain gauge is attached to the abutment to detect the deformation thereof

20. The drum brake as claimed in claim 11, wherein the at least one sensor is based on one of: the anisotropic magnetoresistive effect or the Hall effect.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0022] The invention will be explained in more detail below on the basis of three exemplary embodiments. The drawings show:

[0023] FIG. 1 a brake drum with a first embodiment of the abutment,

[0024] FIG. 2 an enlarged depiction of the abutment of the drum brake shown in FIG. 1,

[0025] FIG. 3 an enlarged depiction of a second embodiment of the abutment, and

[0026] FIG. 4 an enlarged depiction of a third embodiment of the abutment.

DETAILED DESCRIPTION

[0027] FIG. 1 shows a drum brake of a motor vehicle in perspective view, said drum brake comprising a circular carrier plate 1 and two brake shoes 2 and 3, which are arranged concentrically with the central axis of the carrier plate 1.

[0028] The brake shoes 2, 3 are surrounded concentrically by a brake drum (not illustrated here), which is connected to a motor vehicle wheel to be braked, with the result that—when the brake shoes 2, 3 are pressed against this brake drum—the rotating wheel is decelerated (service braking), or a stationary wheel is prevented from rotating (parking braking).

[0029] The brake shoes 2, 3 each have a pressure end and a supporting end, wherein a spreader device 4 is arranged between the opposite pressure ends. This is generally a hydraulically, electromechanically or electrohydraulically actuatable device.

[0030] Between the likewise oppositely situated supporting ends there is a ram 5, which transmits forces from one to the other brake shoe.

[0031] Both the spreader device 4 and the ram 5 are mounted so as to float in the circumferential direction relative to the carrier plate 1, and therefore this is a “duo servo” brake, which has a strong self-energizing effect.

[0032] In order to support the braking forces, which act as frictional forces between the brake shoes 2, 3 and the brake drum, an abutment 6 is provided. This is situated radially outside the spreader device 4, wherein, adjacent to the force introduction points of the spreader device 4, there are furthermore at the ends of the brake shoes 2, 3 pressure heads 7, 8, which are supported on both sides of the abutment 6. Since both the spreader device 4 and the ram 5 are mounted so as to float, the braking force is in each case transmitted only from the trailing brake shoe to the abutment 6.

[0033] Considering the case where the brake drum is rotating counterclockwise in accordance with the illustrated arrow 9, the brake shoe 2 illustrated on the left is the leading brake shoe, and the brake shoe 3 illustrated on the right is the trailing shoe.

[0034] The spreader device 4 pushes the two brake shoes 2, 3 apart, wherein the leading brake shoe 2 is taken along by the brake drum in the direction of rotation thereof relative to the carrier plate 1. The frictional force exerted thereon is transmitted by means of the ram 5 to the trailing brake shoe 3 as well, with the result that the pressure head 8 thereof is supported on the abutment 6.

[0035] The supporting force is measured there, which force is a measure of the braking force and can thus be used to control the spreader device 4.

[0036] For this purpose, in the simplest case, the abutment 6 shown in FIG. 2 consists of a massive but flat component which projects perpendicularly from the carrier plate 1 and is secured thereon, thus enabling the pressure heads 7, 8 to rest on the edges thereof facing in the circumferential direction.

[0037] Here, the abutment 6 comprises a pedestal 10, connected to which via a narrow central web 11 is a base 12, against the edges of which that face in the circumferential direction the pressure heads 7, 8 of the brake shoes 2, 3 can be placed. Since the mutually facing edges of the pedestal 10 and the base 12 extend parallel to one another with a small clearance, two measurement gaps 13, 14 are formed between the pedestal 10 and the base 12, starting from the web 11.

[0038] When the brake drum is rotated counterclockwise in accordance with the illustrated arrow 9, the brake shoe 2 illustrated on the left is a leading brake shoe, and that illustrated on the right is a trailing brake shoe 3. Owing to the frictional forces between the brake shoes and the brake drum, the brake shoes, because they are mounted so as to float, are taken along in the direction of rotation, with the result that the trailing brake shoe 3 is supported on the base 12 of the abutment 6, and the base tilts relative to the pedestal 10, as a result of which—as shown in FIG. 2—the measurement gap 14 facing it widens and the measurement gap 13 facing away from it becomes narrower.

[0039] These changes can be detected by suitable sensors and represent a value for the braking force introduced, which, in turn, can be used to control the spreader device.

[0040] In the case of a different direction of rotation, the functions of the two brake shoes 2, 3 are interchanged, that on the left becoming the trailing shoe and that on the right becoming the leading shoe, with the result that the latter is supported on the base 12 of the abutment 6, as a result of which the left-hand measurement gap 13 facing it is widened and the right-hand measurement gap 14 facing away from it is narrowed.

[0041] Another possibility for the design of the abutment is illustrated in FIG. 3. Extending out of the pedestal 10 secured on the carrier plate 1 is a central web 16, which merges into a transverse web 17, from each of the ends of which a respective arm 18, 19 pointing toward the pedestal 10 emerges. The central web 16, the transverse web 17 and the two arms 18, 19 thus form a T. The pressure heads 7, 8 of the brake shoes 2, 3 are placed against the outer edge of the arms 18, 19, which faces in the circumferential direction.

[0042] Projecting laterally from the central web 16 are two pins 20, 21, which end shortly before the inner edges of the arms 18, 19, in each case forming a measurement gap 13, 14.

[0043] The respective leading brake shoe 2, 3 bends the arm 19 or 18 on which it is supported inward, as a result of which the associated measurement gap 14 or 13 is reduced in size, which, in turn, can be detected by measurement.

[0044] At the same time, the pins 20, 21 serve as overload protectors. If the braking forces become too great, the arms 17, 18 are supported on the associated pin 20, 21.

[0045] A third embodiment, shown in FIG. 4, comprises a pedestal 10 and a base 12 which are connected to one another via two struts 22, 23 situated at the edges, thus forming a frame with a central opening. Emanating from the inner edge of the pedestal 10, which delimits the opening, are two pins 20, 21, which reach as far as the inner edge of the base 12, apart from a measurement gap 13, 14.

[0046] When the base 12 is subjected to a load in the circumferential direction, it shifts parallel to the pedestal 10, with the result that the rectangular frame is transformed into a parallelogram, wherein the base 12 approaches the pedestal 10 and the ends of the pins 20, 21, as a result of which the measurement gaps 13, 14 are correspondingly reduced in size.

[0047] In all the embodiments, there are various possibilities available for measuring the change in the measurement gap. Sensors which utilize the anisotropic magnetoresistive effect (AMR effect) or, alternatively, linear Hall sensors can be used.

[0048] Independently of the measurement of the measurement gap size, the respective change in shape of the abutment can be detected by means of strain gauges.

[0049] The sensors allow determination of the braking torque acting in the drum brake. This is used for controlling the braking effect of the drum brake.

[0050] The foregoing preferred embodiments have been shown and described for the purposes of illustrating the structural and functional principles of the present invention, as well as illustrating the methods of employing the preferred embodiments and are subject to change without departing from such principles. Therefore, this invention includes all modifications encompassed within the scope of the following claims.