BRAKE LINING ARRANGEMENT FOR A VEHICLE DISC BRAKE, AND DISC BRAKE FOR A VEHICLE

Abstract

A brake lining arrangement for a disc brake of a vehicle, including at least one brake lining, which is arranged axially spaced apart from a brake disc in a starting position in the installed state of the disc brake. The brake lining includes a lining carrier plate, on which a friction lining is attached. A spring element positioning the brake lining is arranged on at least one brake lining, which spring element is at least partially formed from a bimetal element and changes the axial distance of the brake lining relative to the brake disc in the starting position as a function of a temperature.

Claims

1-10. (canceled)

11. A brake lining arrangement for a disc brake of a vehicle, comprising: at least one brake lining, which in a starting position is arranged axially spaced apart from a brake disc in the installed state of the disc brake, and wherein the brake lining includes a lining carrier plate, on which a friction lining is attached, wherein a spring element positioning the brake lining is arranged on at least one brake lining, which spring element is at least partially formed from a bimetal element and changes the axial distance of the brake lining relative to the brake disc in the starting position as a function of a temperature.

12. The brake lining arrangement according to claim 11, wherein the spring element, in the installed state of the brake lining arrangement in a disc brake, reduces the axial distance at a predetermined temperature and/or upon falling below the predetermined temperature by way of the bimetal element in order to generate a coefficient of friction between the brake lining and the brake disc.

13. The brake lining arrangement according to claim 12, wherein the spring element includes at least one spring arm, which engages on a rear side of the lining carrier plate facing away from the friction lining, wherein the spring arm is connected to a spring bridge arranged at an angle in relation to the spring arm and to the lining carrier plate.

14. The brake lining arrangement according to claim 13, wherein the spring bridge connects the spring arm to a detent clamp, which surrounds the lateral circumferential surface of at least one lining carrier plate at least partially in the circumferential direction.

15. The brake lining arrangement according to claim 14, wherein the spring element is formed in one piece with the detent clamp.

16. The brake lining arrangement according to claim 13, wherein the spring bridge axially spans the brake linings arranged mutually opposite on the brake disc, wherein the spring bridge connects to one another the spring arms engaging on the respective lining carrier plate.

17. The brake lining arrangement according to claim 16, wherein the spring arms include the bimetal element.

18. The brake lining arrangement according to claim 14, wherein the spring bridge includes the bimetal element.

19. The brake lining arrangement according to claim 16, wherein the spring bridge includes a connection section, via which at least two spring legs extending in the longitudinal direction of the brake lining are connected.

20. A disc brake for a vehicle, comprising: a housing, which spans a brake lining arrangement arranged on a brake disc, wherein the brake lining arrangement includes at least one brake lining, which is guided in a brake support body and can be caused to interact with the brake disc to achieve a braking action, wherein the brake lining arrangement is designed according to claim 11.

21. The brake lining arrangement according to claim 16, wherein the spring bridge includes the bimetal element.

22. The brake lining arrangement according to claim 17, wherein the spring bridge includes the bimetal element.

23. The brake lining arrangement according to claim 17, wherein the spring bridge includes a connection section, via which at least two spring legs extending in the longitudinal direction of the brake lining are connected.

24. The brake lining arrangement according to claim 18, wherein the spring bridge includes a connection section, via which at least two spring legs extending in the longitudinal direction of the brake lining are connected.

Description

BRIEF DESCRIPTION OF THE FIGURES

[0039] Further advantages and possible applications of the present invention result from the following description in conjunction with the exemplary embodiment shown in the drawings.

[0040] In the figures:

[0041] FIG. 1 shows a spring element of a brake lining arrangement according to the invention at a predetermined low temperature;

[0042] FIG. 2 shows a spring element of a brake lining arrangement according to the invention at a higher temperature;

[0043] FIG. 3 shows a spring element of a brake lining arrangement according to the invention at a predetermined low temperature;

[0044] FIG. 4 shows a spring element of a brake lining arrangement according to the invention at a higher temperature;

[0045] FIG. 5 shows a fixed caliber brake which includes a brake lining arrangement according to the invention;

[0046] FIG. 6 shows a spring element of a brake lining arrangement according to the invention; and

[0047] FIG. 7 shows a floating caliper brake which includes a brake lining arrangement according to the invention.

DETAILED DESCRIPTION

[0048] FIG. 1 to FIG. 4 show a brake lining arrangement designated as a whole by the reference numeral 10.

[0049] FIG. 1 shows a brake lining arrangement 10, which in the present case comprises two brake linings 12 spaced apart axially in relation to one another, each of which includes a brake lining carrier plate 14 and a friction lining 16 fastened thereon. In the installed state of the brake lining arrangement 10, a brake disc (not shown in the present case) is arranged between the friction linings 16 facing toward one another, using which brake disc the friction linings 16 are moved during a braking procedure by means of a tensioning device (also not shown in the present case) from a starting position into an engagement position, in which they interact with the brake disc.

[0050] A spring element 18, which in the present case spans both brake linings 12, is arranged on the brake linings 12. The spring element 18 is designed as a leaf spring and includes a spring bridge 20, which connects to spring arms 22 to one another. The spring arms 22 each extend at an angle to the spring bridge 20. In the present case, they extend approximately perpendicularly to the spring bridge 20.

[0051] At its respective ends, the spring element 18 engages on a rear side of the lining carrier plate 14 facing away from the friction lining 16. The spring element 18 is, for example, riveted to the lining carrier plate 14 or it can be engaged, for example, via a detent lug with a detent projection of the lining carrier plate 14.

[0052] In the installed state of the brake lining arrangement 10 in a vehicle disc brake 100, the brake linings 12 are pre-tensioned axially and radially by the present spring element 18. The spring element 18 exerts a restoring force on the brake linings 12 via the spring arms 22, in order to move them back into the starting position, in which the brake linings 12 are spaced apart via an air gap from the brake disc, after a deflection in the direction of the brake disc.

[0053] According to the invention, the spring element 18 is at least partially formed from a bimetal element 24. FIG. 1 and FIG. 2 each show an embodiment of the spring element 18, in which the bimetal element 24 is arranged on the spring bridge 20. In the present case, the spring bridge 20 includes a bimetal strip 24, which is formed from two layers 26, 28 of different metals or alloys that are permanently connected to one another. The layers 26, 28 can be connected to one another, for example, by riveting, welding, adhesive bonding, or rolling. They have different coefficients of expansion. The first layer 26, which has a low coefficient of expansion, is arranged facing away from the brake lining 12 in the present case. The respective other second layer 28 has a higher coefficient of expansion and is arranged opposite to the first layer 26 in the direction toward the brake lining 12. The respective layers 26, 28 change by different distances upon equal temperature change. This is expressed as a bend of the bimetal strip 24 and the spring element 18 therefore deforms accordingly.

[0054] In FIG. 1, the spring element 18 is shown at a predetermined low temperature T. At low temperature T, the second layer 28 having the higher coefficient of expansion contracts more than the first layer 26. The spring bridge 20 thus curves toward the second layer 28, which is also designated as the active component. This deformation causes a reduction of an axial distance between the spring arms 22, which in turn move the respective brake lining 12 in the direction of a brake disc (not shown in the present case). The air gap, i.e., the axial distance between the brake lining 12 and the brake disc in the starting position of the brake lining 12 is thus reduced such that a residual braking torque results between the brake lining 12 and the brake disc. During a braking procedure, the brake lining 12 is deflected in the direction of the brake disc and the spring element 18 is used after the deflection to restore the brake lining 12, in order to reestablish the air gap. Due to the curvature of the bimetal element 24 at the predetermined low temperature T, the spring element 18 can only cause a slight restoring of the brake lining 12. A residual coefficient of friction thus remains between the brake lining 12 and the brake disc and the brake disc is in particular slightly heated in spite of recuperation.

[0055] FIG. 2 shows an illustration of the spring element 18 according to FIG. 1 at a higher temperature T. As shown in the present case, the bimetal element 24 or the spring bridge 20 bends in the opposite direction at temperatures T above the predetermined value. Upon heating, the second layer 28 expands more than the first layer 26. Characteristic concave bending of the bimetal strip 24 thus takes place. This has the result that the respective spring arms 22 of the spring element 18 move away from one another in opposite directions, by which an axial distance between the spring arms 22 is increased. Since the respective brake linings 12 are pulled along by the spring arms 22, the axial distance of the brake lining 12 from the brake disc in the starting position of the brake lining 12 increases. This results in a larger air gap, which is sufficiently large at higher temperatures T that residual coefficients of friction between the brake lining 12 and the brake disc are avoided or strongly reduced. After a deflection of the brake lining 12 in the direction of the brake disc during a braking procedure, the spring element 18 causes greater restoration of the brake lining 12 than at low temperatures T.

[0056] FIG. 3 and FIG. 4 show an alternative embodiment of the spring element 18, in which the respective spring arms 22 include a bimetal element 24. The bimetal element 24 is designed in the present case as a bimetal strip. The first layer 26 having the low coefficient of expansion is arranged on an outside of the spring arms 22, facing away from the brake lining 12, and the second layer 28 having the higher coefficient of expansion is arranged opposite to the first layer 26 on an inside of the spring arm 22 in the direction of the brake lining 12.

[0057] As shown in FIG. 3, the second layer 28 contracts more at the predetermined low temperature T than the first layer 26. The bimetal element 24 bends toward the second layer 28. The spring arms 22 thus curve convexly with respect to the brake lining 12 and a distance between the two spring arms 22 is reduced, wherein the respective spring arms 22 pull the brake linings 12 along in the direction of the brake disc, by which the air gap is reduced. The spring element 18 exerts a restoring force on the brake linings 12, in order to bring them into the starting position after a deflection. The restoration of the brake linings 12 is minor at low temperature T, due to which a residual braking torque results between brake lining 12 and brake disc and the brake disc heats up.

[0058] FIG. 4 shows a spring element 18 according to FIG. 3 at an elevated temperature T. The bimetal element 24 bends in the present case in the opposite direction, because the second layer 28 expands more than the first layer 26. The bimetal element 24 bends in the direction of the first layer 26 or the spring arms 22 been concavely in relation to the brake lining 12, due to which the spring arms 22 move away from one another in opposite directions and a distance between them increases. The spring arms 22 pull along the brake linings 12 and the air gap becomes larger. In this manner, the restoring of the brake linings 12 by the spring element 18 is stronger at elevated temperature T, by which a residual braking torque between brake lining 12 and brake disc is prevented or reduced.

[0059] FIG. 5 shows a view of a disc brake, designated as a whole with the reference numeral 100, for a vehicle. The disc brake 100 includes a frame-like housing 102 having a brake caliper 104, which is designed in the present case as a fixed caliper. The housing 102 is used as a support body for a brake lining arrangement 10 (not shown in the present case), which is arranged in a shaft 106 or a recess of the housing 102. The brake lining arrangement 10 includes two brake linings 12 spaced apart from one another. The reaction forces generated during a braking procedure are transmitted via the lining carrier plates 14 of the respective brake linings 12, which typically consist of metal, to the housing 102.

[0060] In the present case, two spring elements 18 according to the invention are arranged on the brake linings 12 in the shaft 106 of the housing 102. The spring elements 18 are each designed in the present case as a cross-shaped brake lining retainer spring, which is held, for example, by means of holding elements (not shown here), such as a holding pin or holding bracket, a bent wire, or a clamping element in the shaft 106 on the housing 102 in order to enable a secure seat. The brake linings 12 are pre-tensioned inward in the radial direction of the brake disc (not shown in the present case) via the brake lining retainer springs 18.

[0061] The spring element 18 includes spring legs 30 extending parallel to the brake disc (not shown in the present case), which are formed having contact projections 32 at their respective ends, which are supported on housing crossbeams 108 of the brake caliper 104. The spring legs 30 are connected, in particular riveted, to a connection section 34 of a spring bridge 20 of the spring element 18. The spring bridge 20 spans the brake linings 12 and the brake disc axially and connect two spring arms 22 to one another. The spring arms 22 extend nearly orthogonally at an angle to the spring bridge 20 into the shaft 106 and each engage on a rear side of a lining carrier plate 14 of the brake lining 12.

[0062] The bimetal element 24 is formed on the spring bridge 20 and/or the spring arms 22. As described above in FIGS. 1 to 4, the shape of the bimetal element 24 and thus the shape of the spring element 18 changes as a function of a temperature T, wherein the axial distance in the starting position or the air gap between the brake lining 12 and the brake disc is variable via the shape change of the spring element 18. In other words, the starting position of the brake lining 12 is influenced as a function of the temperature of the spring element 18. The spring element 18 is used to ensure a small air gap having an accompanying residual braking torque for heating the brake disc at cold temperatures T. At warm temperatures T, the spring element 18 enlarges the air gap in order to reduce or entirely avoid a residual braking torque.

[0063] FIG. 6 shows an alternative embodiment of a spring element 18. In the present case, the spring element 18 is formed in one piece with a detent clamp 36, via which the spring element 18 is arrangeable on a brake lining 12, in order to act with a restoring force on the brake lining 12. Alternatively, the detent clamp 36 and the spring element 18 can be formed in two pieces and can be connected to one another via a connecting element.

[0064] The detent clamp 36 is formed in the present case having two legs 38, which are connected to one another via a central section 40, which spans a brake disc (not shown in the present case). The legs 38 each press against a lateral circumferential surface 42 of a lining carrier plate 14 (not shown in the present case) and extend along the lateral circumferential surface 42. In the present case, the legs 38 each have a contour which engages, for example, in recesses of the circumferential surface 42 of the lining carrier plate 14. The detent clamp 36 at least partially grasps around the lining carrier plate 14 in the circumferential direction. The detent clamp 36 supports the brake lining 12 in the installed state of the brake lining arrangement 10 in a disc brake 100 against circumferential forces and holds it in position in the radial direction with respect to the brake disc by pre-tension.

[0065] The spring element 18 includes a spring arm 22, which engages on the lining carrier plate 14. The spring arm 22 can be riveted with the lining carrier plate 14, for example. The spring arm 22 engaging on the lining carrier plate 14 is connected via a spring bridge 20 to the detent clamp 36. The spring element 18 spans and clamps around the lateral circumferential surface 42 of the lining carrier plate axially in the present case and the spring arm 22 extends in the direction of the detent clamp 36.

[0066] In the present case, the spring bridge 20 includes the bimetal element 24. The material having the higher coefficient of expansion or the second layer 28 is arranged in the direction of the brake lining 28 and the material having the lower coefficient of expansion or the first layer 26 is arranged facing away from the brake lining 12. At a high temperature T, as shown in the right illustration of FIG. 6, the second layer 28 expands more strongly in contrast to the first layer 26. The spring bridge 20 thus bends in the direction of the first layer 26 or away from the rear side of the lining carrier plate 14. The axial distance between the brake lining 12 and the brake disc thus increases, i.e., the starting position of the brake lining 12 moves away from the brake disc. As a result, the air gap increases, due to which residual coefficients of friction between the brake lining 12 and the brake disc are eliminated or largely avoided.

[0067] At a low temperature T, as shown in the left illustration of FIG. 6, the second layer 28 contracts more than the first layer 26. The spring element 18 thus curves in a direction toward the second layer 28 and displaces the brake lining 12 in the direction of the brake disc. This has the result that the axial distance of the brake lining 12 from the brake disc in the starting position of the brake lining 12 is reduced. Possible restoration of the brake lining 12 in the axial direction after a deflection of the brake lining 12 is thus reduced, and the air gap is reduced such that a residual braking torque results between the brake lining 12 and the brake disc, due to which the brake disc heats up slightly.

[0068] FIG. 7 shows a disc brake 100, comprising a frame-like housing 102, the main body of which is designed in the present case as a floating caliper or fist caliper, and a brake support body or a brake carrier 110, which guides or mounts the brake linings 12 of a brake lining arrangement 10 with play. The brake lining arrangement 10 includes two brake linings 12 in the present case, which are each arranged in their starting position via an axial distance on a brake disc (not shown in the present case). A tensioning device is received in the housing 102, via which the brake linings 12 are movable toward the brake disc during a braking procedure.

[0069] A spring element 18 according to the invention, as described above in FIG. 6, is arranged on the brake linings 12. The spring element 18 is arranged via a detent clamp 36 on the brake lining 12. The detent clamp 36 is at least partially arranged between the brake carrier 110 and the brake linings 12, in particular a lateral circumferential surface 42 of the lining carrier plate 14 of the brake lining 12. The detent clamp 36 is arranged on a transverse element 112 of the brake carrier 110 and includes legs 38 which can engage around, for example, projections formed on the transverse element 112. The detent clamp 36 can be formed on the brake carrier 110 or can be permanently connected thereto.

[0070] The detent clamp 36 extends around the lateral circumferential surface 42 of a lining carrier plate 14 of a brake lining 12 in the circumferential direction. The legs 38 of the detent clamp 36 each extend here along the lateral circumferential surface 42 of the lining carrier plate 14. The detent clamp 36 supports the brake lining 12 in the installed state of the brake lining arrangement 10 in the disc brake arrangement 100 against circumferential forces and holds it in position in relation to the brake disc by pre-tension in the radial direction.

[0071] The spring element 18 according to the invention exerts a restoring force on the brake lining 12 after a deflection of the brake lining 12. The spring element 18 is connected via a spring arm 22 to a rear side of the lining carrier plate 14, wherein the spring arm 22 is arranged on the detent clamp 36 via a spring bridge 20 (not shown here), which is at least partially formed using a bimetal element 24, on which the detent clamp 36 is arranged. The spring element 18 curves at low temperature T in the direction of the lining carrier plate 14, due to which the starting position of the brake lining 12 moves in the direction of the brake disc and the air gap is sufficiently small that a residual coefficient of friction is present between the brake linings 12 and the brake disc. At higher temperatures T, the bimetal element 24 of the spring element 18 bends in the opposite direction. The spring element 18 thus pulls the brake linings 12 farther apart in a starting position and an air gap without residual coefficients of friction results.