阅读说明：本技术 盘式制动器以及制动衬片 (Disk brake and brake lining ) 是由 A·佩特施克 M·阿德龙 J·弗里克 J·施罗普 于 2020-03-27 设计创作，主要内容包括：本发明涉及一种用于商用车的可被电操纵的或可被气动操纵的盘式制动器,其包括以下特征：——制动盘(4),该制动盘具有优选的旋转方向(D)；——制动器支架(2)；——制动钳(3),该制动钳在所述制动器支架(2)上可移动地被引导；——制动施加侧的制动衬片(5)和反作用侧的制动衬片(6),它们在所述制动器支架(2)的制动施加侧的衬片安装槽(203)中和在反应侧的衬片安装槽(204)中平行于制动盘旋转轴线(A4)可移动地设置；——制动施加装置,该制动施加装置具有单个的压力活塞(304),该压力活塞具有中轴线并且压力活塞在朝向所述制动施加侧的制动衬片的端部上具有承压件(306),该承压件以压力面(307)作用到所述制动施加侧的制动衬片(5)的对应的支座面(53)上,从而在制动器施加制动时在压力面(307)与支座面(53)之间构成作用面,——所述制动施加侧的制动衬片和反作用侧的制动衬片在周向方向上相对于制动盘和活塞(304)的中轴线定心地定向,——作用面在周向方向上相对于制动盘(4)的优选的旋转方向和活塞(304)的中轴线在出口侧偏移,在盘式制动器施加制动时压力面(304)和支座面(53)在所述作用面处彼此贴靠。(The invention relates to an electrically or pneumatically actuable disc brake for a utility vehicle, comprising the following features: -a brake disc (4) having a preferred direction of rotation (D); -a brake carrier (2); -a brake caliper (3) which is guided movably on the brake carrier (2); -a brake application-side brake lining (5) and a reaction-side brake lining (6) which are arranged movably parallel to the brake disc axis of rotation (a4) in a brake application-side lining mounting groove (203) and in a reaction-side lining mounting groove (204) of the brake carrier (2); -a brake application device having a single pressure piston (304), the pressure piston has a central axis and the pressure piston has a pressure-bearing part (306) on the end of the brake lining facing the brake application side, the pressure-bearing element acts with a pressure surface (307) on a corresponding abutment surface (53) of the brake lining (5) on the brake application side, so that, when the brake is applying the brake, an active surface is formed between the pressure surface (307) and the seat surface (53), wherein the brake application-side brake lining and the reaction-side brake lining are aligned in the circumferential direction in a centered manner with respect to the center axis of the brake disk and the piston (304), wherein the active surface is offset in the circumferential direction on the outlet side with respect to the preferred direction of rotation of the brake disk (4) and the center axis of the piston (304), the pressure surface (304) and the seat surface (53) abut against each other at the active surface when the disc brake applies the brake.)

1. An electrically or pneumatically actuable disc brake for a utility vehicle, comprising the following features:

-a brake disc (4) having a preferred direction of rotation (D),

-a brake support (2),

a brake caliper (3) which is guided movably on the brake carrier (2),

-a brake application-side brake lining (5) and a reaction-side brake lining (6) which are arranged movably parallel to the brake disk axis of rotation (A4) in a brake application-side lining mounting groove (203) and in a reaction-side lining mounting groove (204) of the brake carrier (2),

-a brake application device having a single pressure piston (304) which has a center axis (M1) and which, at the end of the brake lining facing the brake application side, has a pressure piece (306) which acts with a pressure surface (307) on a corresponding seat surface (53) of the brake lining (5) on the brake application side, so that an active surface is formed between the pressure surface (307) and the seat surface (53) when the brake applies the brake, the brake lining on the brake application side and the brake lining on the reaction side being oriented in the circumferential direction in a centered manner with respect to the center axis (M) of the brake disk and the piston (304),

it is characterized in that the preparation method is characterized in that,

-the active surface, at which the pressure surface (304) and the seat surface (53) abut against each other when the disc brake applies the brake, is offset in the circumferential direction with respect to the preferred direction of rotation of the brake disc (4) and the centre axis (M) of the piston (304) on the outlet side.

2. The disc brake of claim 1, characterized in that the brake linings on the brake application side and the brake linings on the reaction side are arranged movably in a lining mount groove (203) on the brake application side of the brake carrier (2) and in a lining mount groove (204) on the reaction side parallel or substantially parallel to the brake disc axis of rotation (a 4).

3. The disc brake of claim 1 or 2, characterized in that the pressure piece (306) is designed to act on the brake lining (5) on the brake application side at least when the disc brake applies the brake.

4. The disc brake of claim 1, 2 or 3, characterized in that the brake disc (4) preferably has a diameter of 330mm or more.

5. The disc brake of any one of the preceding claims, characterized in that the brake caliper (3) and the brake carrier (2) each straddle the upper edge of the brake disc (4) in a frame-like manner, wherein a central opening (303) for lining replacement is provided in the brake caliper (3).

6. The disc brake of any one of the preceding claims, characterized in that the brake linings (5, 6) each have a back plate (51, 61) and a friction material (52, 62), and the friction material (52, 62) and/or the back plate (5, 6) are oriented in a centered manner in the circumferential direction with respect to the brake disc (4).

7. The disc brake of any one of the preceding claims, characterized in that the back plate (51) has a series of ribs (54) and voids/recesses (55).

8. The disc brake of any one of the preceding claims, characterized in that the lining-mounting groove of the brake carrier is oriented in the circumferential direction centrally with respect to the brake disc (4).

9. The disc brake of any one of the preceding claims, characterized in that the pressure-bearing piece (306) has a projection which has a pressure surface (307) and which is arranged offset in the circumferential direction on the outlet side with respect to the preferred direction of rotation (D) of the brake disc (4).

10. The disc brake of any one of the preceding claims, characterized in that the seat surface (53) of the back plate is arranged offset in the circumferential direction on the outlet side with respect to the preferred direction of rotation (D) of the brake disc (4).

11. The disc brake of any one of the preceding claims, characterized in that the seat surface (53) of the back plate (51) of the brake lining (5) on the brake application side is constituted by a shoulder of the back plate.

12. The disc brake of any one of the preceding claims, characterized in that the shoulder is constituted by an element mounted on the back plate (51) of the brake lining (5) on the brake application side.

13. The disc brake of any one of the preceding claims, characterized in that the element mounted on the back plate (51) of the brake lining (5) on the brake application side is a sheet-metal element fixed to the back plate.

14. The disc brake of any one of the preceding claims, characterized in that the back plate (54) of the brake lining has a recess (56a) which is situated under the pressure piece, completely or partially displaced on the inlet side relative to the rotor axis of rotation (M), so that the back plate (54) does not contact the pressure piece in the region of the recess and the brake lining contacts the pressure piece in the region next to the recess during braking.

15. The disc brake of any one of the preceding claims, characterized in that the center of gravity and the effective center of gravity of the entire lining (5) and the friction material (52) are oriented in the circumferential direction relative to the center axis M1 of the pressure piston (304) by distributing the recesses (55) and/or the ribs (56) on the back plate (51).

16. The disc brake of any one of the preceding claims, characterized in that the brake application device is arranged in the brake caliper (3) on a brake application side (301) of the brake disc (4), and the brake caliper (3) surrounds a circumferential region engaging the brake disc in a frame-like manner.

17. Brake lining for a disc brake according to one of the preceding claims, characterized in that it has a single seat surface (53) which is eccentric with respect to its center of gravity (M5) for a pressure piston (304) having a pressure surface (307).

18. Brake lining for a disc brake according to one of the preceding claims, characterized in that it has a single eccentric seat surface (53) and that it is of substantially semicircular or completely semicircular design.

19. Brake lining for a disc brake according to one of the preceding claims, characterized in that its back plate (54) has a recess (56a) which is located below the pressure piece, completely or partially displaced on the inlet side relative to the brake disc axis of rotation (M), so that the back plate (54) does not contact the pressure piece in the region of the recess.

20. Brake lining for a disc brake according to one of the preceding claims, characterized in that the interspace (56a) has a circular segment shape.

21. Brake lining for a disc brake according to one of the preceding claims, characterized in that the center of gravity and the effective center of gravity of the entire lining (5) and the friction material (52) are oriented in the circumferential direction relative to the center axis M1 of the pressure piston (304) by the arrangement of the recesses (55) and/or ribs (56) on the back plate (51).

22. Vehicle having at least one wheel axle, wherein the wheel axle has a main direction of rotation relative to a main direction of travel of the vehicle or the main direction of travel, and wherein the wheel axle has at least one disc brake associated with a left end (and a wheel) of the wheel axle on a vehicle left side (1), and wherein the wheel axle has at least one disc brake associated with a right end (and a wheel) of the wheel axle on a vehicle right side (1), wherein the disc brake on the vehicle left side (1) and the disc brake on the vehicle right side (1) are each configured according to one of claims 1 to 16.

Technical Field

The invention relates to a disc brake according to the preamble of claim 1 and to a brake lining for such a disc brake.

Background

EP2392835B1 is mentioned as prior art.

It is known from this prior art to introduce structural measures for preventing the oblique wear of the lining in a disc brake of a heavy-duty utility vehicle having a brake carrier and a sliding brake caliper and a brake application device with only a single pressure piston.

In this case, one or both brake linings are usually offset in the circumferential direction relative to the brake disk on the inlet side or on the outlet side (relative to the preferred direction of rotation of the brake disk).

This is generally relatively complex in construction, since the lining mount slots are usually correspondingly offset in the brake carrier. It is also known to make a corresponding offset by means of a chamfer or bevel on the friction material, but this reduces the effective friction surface between the friction material and the brake disc.

Disclosure of Invention

The object of the present invention is to provide an alternative measure for reducing the effect of the oblique wear of the brake lining, which does not require a displacement of the lining in the circumferential direction.

The invention solves the stated object by the subject matter of claim 1 and the subject matter of claim 17.

According to claim 1, an electrically or pneumatically actuable disc brake for a utility vehicle is provided, which is also preferably actuated electrically or pneumatically in operation and has the following features: a brake disc having a preferred direction of rotation; a brake bracket; a brake caliper which is guided movably on a brake carrier; a brake lining on a brake application side and a brake lining on a reaction side; a brake application device having a single pressure piston, which has a center axis and which, at the end of the brake lining facing the brake application side, has a pressure-bearing part, which acts with a pressure surface on a corresponding abutment surface of the brake lining on the brake application side, so that, when the brake is applied, an active surface is formed between the pressure surface and the abutment surface, wherein the brake lining on the brake application side and the brake lining on the reaction side are aligned (or centered) in the circumferential direction with respect to the center axis of the brake disk and the piston, wherein the active surface is offset in the circumferential direction with respect to a preferred direction of rotation of the brake disk and the center axis of the piston on the outlet side, and the pressure surface and the abutment surface bear against one another on the active surface when the disk brake is applied with braking.

A particular advantage of this embodiment is that, even in disc brakes which have only a single pressure piston and in which the brake linings are both aligned in a centered manner in the circumferential direction with respect to the brake disc, the oblique wear of the brake linings can be suppressed simply by changing the pressure-bearing piece and/or the back plate of the brake lining without an offset of the lining and/or its associated lining installation groove, so that the active surface is positioned eccentrically in the circumferential direction or is not aligned centrally with respect to the brake disc. This measure can be implemented simply in the case of a complementary fitting method or by simple structural changes of elements such as the pressure piece and/or the brake lining on the brake application side.

Preferably, the pressure piston has a first, preferably cylindrical or partially cylindrical section and a pressure-receiving part for acting on the brake lining on the brake application side at least when the disc brake applies the brake. Furthermore, it can be provided that the brake disk has a diameter of 15 ″ or more, since in such a sliding caliper disk brake with a relatively large disk diameter it is particularly advantageous that a reduction in the angular wear is possible without the complex structural offset of the lining installation groove and without the effective lining friction surfaces also being reduced by chamfers or the like.

It can be provided that the brake application-side brake lining and the reaction-side brake lining are arranged in a brake application-side lining mount groove and (that is to say or) in a reaction-side lining mount groove of the brake carrier. In addition, it can be advantageously provided that the brake caliper and the brake carrier each straddle the upper edge of the brake disk in a frame-like manner, wherein a central opening for pad replacement is provided in the brake caliper. This means that the brake lining is inserted into the brake carrier through the central opening of the brake caliper and is pulled out again in the opposite direction.

In such a brake, it is also very advantageous according to the invention that an offset of the brake lining in the circumferential direction can be dispensed with, so that the length of the opening of the brake caliper in the circumferential direction can be substantially equal to the lining length.

For this purpose, it can also be advantageously provided that the lining mounting groove of the brake carrier is aligned in a centered manner in the circumferential direction relative to the brake disk.

It can be provided that the brake linings each have a back plate and a friction material, wherein preferably the friction material and/or the back plate is/are aligned in a centered manner in the circumferential direction with respect to the brake disk. The described embodiments are again very advantageous, since they ensure a particularly large friction surface and a particularly simple design of the back plate. Particularly preferably, the back plates and the friction material of the two brake linings of the disc brake are oriented in the circumferential direction relative to the piston.

The present invention can be advantageously improved in structure.

In order to achieve an offset of the outlet side of the active surface, it can therefore be provided that the pressure receiving element has a projection which has a pressure surface and which is arranged offset on the outlet side in the circumferential direction with respect to a preferred direction of rotation of the brake disk.

However, in order to achieve an offset of the outlet side of the active surface, it can also be provided that the seat surface of the back plate is arranged offset on the outlet side in the circumferential direction with respect to the preferred direction of rotation of the brake disk.

Finally, in order to achieve an offset of the active surface on the outlet side, it can also be provided that the abutment surface of the back plate offset on the outlet side is formed by a shoulder of the back plate. This can be constituted simply by the elements mounted on the back plate. In this case, it can be further easily provided that the elements mounted on the back plate are sheet-metal elements which are fixed to the back plate.

The invention further provides a brake lining for a disc brake according to one of the claims relating to the disc brake, which brake lining has a preferably single, eccentric seat surface with respect to the center of gravity of the brake lining for a pressure piston having a pressure surface. In this way, the brake lining is advantageously functionally improved and the offset of the outlet side of the active surface can be realized in a particularly simple manner. For this purpose, it can be provided, for example, that the single eccentric bearing surface is of substantially semicircular design or of completely semicircular design.

The invention also provides a vehicle having at least one wheel axle, wherein the wheel axle has a main direction of rotation relative to a main direction of travel of the vehicle or the main direction of travel, and the wheel axle has, on the left side of the vehicle, at least one disc brake associated with a left end of the wheel axle (and a wheel), and the wheel axle has, on the right side of the vehicle, at least one disc brake associated with a right end of the wheel axle (and a wheel), wherein the disc brake on the left side of the vehicle and the disc brake on the right side of the vehicle are each configured according to one of claims 1 to 13. The brake discs of the two disc brakes can be connected to the wheel axle in a rotationally fixed manner.

In this way, the disk brake according to the invention is advantageously provided and used on the vehicle as a disk brake on the left side of the vehicle and a disk brake on the right side of the vehicle. The vehicle has a plurality of axles with left and right wheels. At least one or more of these wheel axles is provided with a disc brake according to the invention in the end region.

In this case, the respective left-hand disc brake and the respective disc brake on the right-hand side of the vehicle differ according to an advantageous variant only in terms of the brake lining and its back plate.

In the case of a disk brake on the right-hand side, for example, in the case of a disk brake on the brake application side, the recess of the brake lining on the brake application side below the pressure surface is therefore completely or predominantly oriented, in the installed state, more toward one side of the center axis, for example, the right inlet side, and, in the case of a corresponding disk brake on the left-hand side, in the case of a brake lining on the brake application side, is completely or predominantly oriented, in the installed state, more toward the other side of the center axis, for example, the left side. At this time, the brake application is performed from the center of the vehicle outward (rightward or leftward) toward the corresponding wheel using the brake application device. The main driving direction is forward driving. The forward travel determines the main direction of rotation of the brake disc. In this case, it can be advantageous to mark whether a brake lining for the disc brake is provided on the left side of the vehicle or whether a brake lining for the disc brake is provided on the right side of the vehicle, for example, by providing the brake lining for the brake application side of the disc brake located on the left side of the vehicle in the direction of travel and the brake lining for the brake application side of the disc brake on the right side of the vehicle with suitable markings, for example "L" for the "disc brake on the left side of the vehicle" and "R" (in the direction of travel of the vehicle) for the "disc brake on the right side of the vehicle".

For electric or pneumatic actuation, the disk brake can be provided with or have an actuator. The actuator can have an electric motor, for example for the purpose of electric actuation, and preferably a transmission which acts on the brake application device, or can have a compressed air cylinder, for example for the purpose of pneumatic actuation, which is preferably actuated together with a piston rod of the disc brake. The disc brake thus becomes an electrically or pneumatically operated disc brake, respectively.

Drawings

The invention is described in detail below with the aid of examples. The invention is not shown exhaustively by the embodiments described but may be implemented in other ways not shown within the scope of the claims. In the drawings:

fig. 1 shows a view of a part of a brake caliper thereof, a disc brake with a brake carrier, a brake caliper and a brake application device in a viewing direction to a pressure piece of the brake application device;

fig. 2 shows a perspective view of a pressure piston with a pressure-bearing piece;

fig. 3 shows a plan view of an arrangement with a brake carrier, brake linings and pressure pistons;

fig. 4 shows different views of the brake lining on the brake application side in a) and b); and

fig. 5 shows different views of an alternative design of the brake lining on the brake application side in a) and b);

fig. 6 shows a perspective view of the brake lining on the brake application side of the disc brake on the left side of the vehicle in a) with a circular surface showing the preferably flat pressure surface of the pressure receiving means acting on the back plate, in b) the brake lining on the brake application side of the disc brake on the left side of the vehicle, and in c) the brake lining on the brake application side of the disc brake on the right side of the vehicle, wherein the recess or recess of the brake lining on which the pressure receiving means acts is located further to the left on the back plate in the disc brake on the left side and further to the right in the disc brake on the right side.

Detailed Description

The individual features of the disk brake described below do not necessarily have to be used in each case in mandatory combination with all other features of the embodiments. Instead, other features of the disk brake can also be combined individually or in other embodiments of the disk brake according to the invention. Furthermore, the embodiments shown may also be modified in detail.

Fig. 1 and 3 show the elements and the structural assembly of a disc brake 1 having a brake carrier 2, a brake caliper 3 and a brake disc 4. The brake caliper 3 is guided displaceably on the brake carrier 2. Accordingly, it relates to a sliding caliper disc brake. Disc brakes are brakes for commercial vehicles. A vehicle may have a plurality of such disc brakes. The right-hand disc brake and the left-hand disc brake of the vehicle may each be constructed according to the invention. The disk brake 1 is designed for actuation by a pneumatically driven actuator or by an electrically driven actuator. The actuator can be, for example, a brake cylinder which acts on a brake lever (not shown here) by means of a piston rod.

The brake disc 4 may preferably have a diameter of 330mm or more, again preferably up to 432 mm. The brake application means are arranged in the brake caliper 3 on the brake application side 301 of the brake disk 4.

The brake caliper 3 rides in a frame-like manner on the upper edge of the brake disc 4. The brake disc 4 has a preferred direction of rotation D (fig. 3). The rotational direction corresponds to the rotational direction of the wheels when the vehicle is traveling forward.

The brake carrier 2 likewise has a frame-like shape and surrounds the upper edge of the brake disk 4. The brake carrier is fixed to a vehicle-side fastening (not shown here). This fixing is usually performed on the brake application side of the disc brake. The brake carrier 2 and the brake caliper 3 have a brake application side 201, 301 and a reaction side 202, 302, respectively. Further, the brake bracket 2 has a brake application side lining attachment groove 203 and a reaction side lining attachment groove 204.

In view of the preferred direction of rotation D of the brake disk 4 during forward travel, the brake carrier has an inlet-side transverse strut 205 and an outlet-side transverse strut 206. The lateral strut is substantially perpendicular to the brake application side longitudinal strut 207 and the reaction side longitudinal strut 208. Each of the two lining mount grooves 203, 204 also has an inlet-side bracket angle 209, 210 and an outlet-side bracket angle 211, 212, wherein the respective brake lining 5, 6 is supported in the circumferential direction during braking during forward travel. The term "circumferential direction" relates to the movement of the brake disc 4 in the direction D. A part (an annular section) of the brake disk 4 protrudes through the brake carrier 2 upwards from the latter or at least into the latter.

By "oriented in the circumferential direction" is meant that the respective element is oriented concentrically and centrally with respect to the brake disc portion in the circumferential direction. The element is therefore located centrally in front of the respective annular section of the brake disk and does not move eccentrically relative to this section. For this purpose, the element can have a center plane which is oriented radially with respect to the axis of rotation a4 of the brake disk and can also be provided such that the center of gravity of the element (e.g. brake lining 5 or 6) also runs through the center plane parallel to the axis of rotation a4 of the brake disk 4.

The brake linings 5, 6 can preferably be inserted into the lining mount grooves 203, 204 through an opening 303 of the brake caliper and are already used in fig. 3. The brake linings 5, 6 each have a back plate 51, 61 and a friction material 52, 62. The friction materials 52, 62 are each oriented toward the brake disk 4. The brake linings 5, 6 can be displaced parallel to the brake disk axis of rotation a. In fig. 3, the axis of rotation a is located below the center axis M of the pressure piston 304 parallel to it. The movement of the brake linings 5, 6 takes place during braking and, if necessary, in order to compensate for lining wear. The brake linings 5, 6 and preferably their friction materials 52, 62 and preferably also their back plates 51, 61 can be aligned in a centered manner in the circumferential direction relative to the brake disk 4. Preferably, the center of gravity of the brake linings 5, 6 and preferably their friction materials 51, 61 and their backing plates 52, 62 are thus centered in the circumferential direction on these respective elements. The brake caliper 3 has a central, central opening 303, into which the circumferential edge of the brake disk 4 is sunk. Through this opening, the brake linings 5, 6 can be inserted into the lining mount grooves 203, 204 during lining replacement.

The brake caliper 3 has a brake application device on its brake application side (not shown or visible here, except for the pressure piston 304). The brake application means may be provided in an opening of the caliper 3. The brake application device is used to convert a compacting motion of an element of the actuator into a brake application motion. For this purpose, the brake application movement can have one or more elements, such as levers, bearings and/or crossbars, which act on the pressure piston. The design of such brake application devices is known per se in a very different manner and is therefore not described in detail here. Otherwise, the brake application devices are not shown here with individual pressure pistons 304 (see fig. 1, 2 and 3). The pressure piston 304 may have a cylindrical or partially cylindrical section 305. Furthermore, the segments have, at their end facing the brake lining 5, a separate pressure piece 306 here, which serves to act on the brake lining 5 on the brake application side at least when the disc brake applies the brake.

A pressure surface 307 is formed on the free end of the pressure-bearing part 306. The pressure piece 306 can be formed integrally with the cylindrical section 305 or can be mounted thereon. The cylindrical section 305 can be configured as a pipe section, in particular as a threaded pipe section. The pressure piece 306 can also be designed as a pressure piece region which is otherwise indistinguishable from the section 305 and to some extent only forms the free end region thereof.

The back plate 51 of the brake lining 5 on the brake application side has a seat surface 53 corresponding to the pressure surface on which the pressure surface 304 is supported during braking. The back plate 51 can otherwise be of planar design, but can alternatively also have ribs 54 and recesses 55 (fig. 4a, 4b, fig. 5a, 5 b). They can be distributed (if appropriate with the ribs 54a forming the seat surface 53 in fig. 4) overall in such a way that the center of gravity M5 of the brake lining 53 and preferably also the center of gravity of its lining material or friction material and the back plate extend through a center axis M51, which center axis M51 lies in the center plane and preferably the symmetry plane of the brake lining (with respect to the outer contour, except for deviations, for example, of the recesses for sensors or the like). These center of gravity lines are therefore preferably aligned in the circumferential direction, centered with respect to the brake disk.

During braking, the pressure piston 304 is pressed by the pressure-receiving element 306 via the pressure surface 307 against the back plate 51 of the brake lining 5 on the brake application side. This moves the brake lining 5 on the brake application side in its lining installation groove 203 on the brake application side in the direction of the brake disc 202 until the brake lining 5 on the brake application side comes into frictional contact with the surface of the brake disc 4 and brakes the brake disc. During braking, the brake caliper 3 is displaced counter to the direction of movement of the pressure piston 304 as a result of the brake application process, whereby the brake linings 6 on the reaction side are likewise pressed against the brake disk 4 by means of their friction material 62. The brake caliper 3 preferably acts over the entire surface area on the back plate 62 of the brake lining 6 on the reaction side, which is thus likewise displaced in its support-mounting groove 204 in the axial direction parallel to the axis of the brake disk 4 in the direction of the brake disk 4. In this way, the rotational speed of the brake disc 4 is reduced during braking and the vehicle provided with the corresponding disc brake is braked.

Within the framework of this document, the surface against which the pressure surface 307 and the seat surface 53 bear on each other when the brake is applied is referred to as the active surface (see fig. 1, 2 and 3). If additional elements, for example a metal sheet 56 (see fig. 4), are provided on the back plate, via which the pressure piston 304 acts on the back plate 51, said elements, in particular the metal sheet, are counted as the back plate 51 and are understood within the scope of this document as elements of the brake linings 5, 6.

Stipulating: the contact surfaces, against which the pressure surface 304 and the seat surface 53 bear when the disc brake applies the brake, are not centered in the circumferential direction with respect to the brake disc, but are oriented offset in the rotational direction on the outlet side with respect to the brake disc. Furthermore, it can be provided that the active surface is not aligned in a centered manner in the circumferential direction relative to the center axis M304 of the pressure piston 304, but is arranged offset (completely or largely) relative to this center axis M304 on the outlet side in the preferred direction of rotation of the disc brake 1.

This is apparent from fig. 3 in that the force line F or force vector of the force with which the pressure piston 304 acts on the brake lining 5 is correspondingly offset in the outlet direction with respect to the center axis M304 and the rotor axis of rotation a 4.

According to a preferred embodiment, the center axis M304 of the single pressure piston 304 can be located in the middle of the two center axes M213, M214 of the slide bearings 213, 214 of the disc brake 1, with which slide bearings 213, 214 the brake caliper 3 is guided so as to be movable relative to the brake carrier 2. The center axes M213, M214 are preferably equally far radially from the brake disk axis of rotation a 4.

The movement of the action face between the brake lining 5 and the pressure receiving member 306 in the circumferential direction (with reference to the brake disc 4) effectively and simply suppresses the inclined wear.

It is particularly advantageous if the brake linings 5, 6 and in particular their friction surfaces and the lining installation grooves do not have to be offset relative to the center axis M304 of the pressure piston 306. Both of them remain centred in the circumferential direction with respect to the brake disc 4 and also oriented with respect to the central axis M304 of the piston 304. The center of gravity (of friction linings 52, 62 and/or back plates 51, 61) preferably extends through the plane spanned by M304 and a 4.

A particular advantage of this embodiment is that, even in disc brakes which have only a single pressure piston 304 and in which both brake linings 5, 6 are aligned in a centered manner in the circumferential direction with respect to the center axis M304 and the brake disc 4, the oblique wear of the brake linings can be suppressed simply by changing the pressure receiving element 306 and/or the back plate 51 of the brake lining 5 without a deflection of the linings 5, 6 and/or their associated lining mounting grooves 203, 204 such that the active surfaces are positioned eccentrically in the circumferential direction or are not aligned centrally with respect to the brake disc. This measure can be implemented simply in the complementary fitting method or by simple structural changes of the elements, such as the pressure piece 306 and/or the brake lining 5 on the brake application side.

The pressure surface 307 of the pressure piston 304 presses against the back plate 51 of the brake lining 5 on the brake application side during braking only in the region of the active surface.

The pressure piston 304 has a central axis M304. The lining mounting grooves 203, 204 are preferably each formed symmetrically with respect to this center axis M304 and with respect to a plane defined by the center axis M304 and the rotor axis of rotation a 4. This means that the bracket angles 209, 210 on the inlet side and on the outlet side; 211. the bearing surfaces on 212 are each equally distant from the center axis M304. The friction linings 52, 62 can also be designed symmetrically with respect to this center axis. Their center of gravity may thus lie on the plane defined by M304 and a 4. This can mean, in particular, that the friction linings 5, 6 are centered with respect to the center axis M304 of the pressure piston 304 in the circumferential direction of the brake disk with respect to the pressure piston 304 and the brake disk 4 and are not offset with respect to the preferred direction of rotation of the brake disk 4 and the brake disk 4 on the inlet side or the outlet side.

The pressure-receiving element 306 acts upon the back plate 51 of the brake lining 5 on the brake application side in the active area with a force vector F in the force line aligned therewith during braking. The bearing piece 306 can be oriented concentrically in the circumferential direction or in the direction of rotation in the disc brake.

The friction material 52 of the brake lining 5 on the brake application side and the friction material 62 of the brake lining 6 on the reaction side are each displaced by the same amount in the direction of the inlet side (at 205) only with respect to the force vector F. The influence of the oblique wear of the brake linings 5, 6 can thereby be suppressed in a simple manner.

One or more constructional measures are required to form an eccentric active surface between the pressure piece 306 and the brake lining 5 on the brake application side.

Thus, in order to form an outlet-side offset active surface between the pressure piece 306 and the brake lining 5 on the brake application side, according to a variant, the pressure piece can have a shoulder 308 facing the brake lining 5 (fig. 1 and 2) in the sense that it is offset toward the outlet side and not symmetrical with respect to the plane formed by M304 and a 4.

The shoulder 308 can be designed in the form of a ring segment. However, the shoulder can also be of substantially semi-cylindrical design, for example. The shoulder can also be designed in a different manner, for example rectangular in the region of the seat surface 53. This shoulder thus acts on the seat surface 53. The seat surface can be designed correspondingly, i.e. for example in the form of a likewise annular segment. However, the seat surface can also be designed in a different manner, for example round or rectangular.

However, according to a further variant, for example, the pressure surfaces 307 of the pressure-bearing part 304 may also be offset in the circumferential direction not on the outlet side, but rather concentrically and/or symmetrically with respect to the center axis, and the seat surfaces 53 of the brake linings 5 may be designed such that the active surfaces are still displaced on the outlet side, so that the effective force vector F1 is offset on the outlet side.

Thus, according to a variant, the pressure face 307 of the pressure-bearing member 306 can be displaced eccentrically on the outlet side. However, the seat surface 53 may be movable on the outlet side. Both faces can also be offset on the outlet side.

For this purpose, it is conceivable that a pressing contour which is eccentric with respect to the surrounding surface of the back plate 51 and which is eccentric with respect to the center axis M of the pressure piston 304 and which projects with respect to at least one surrounding area is provided as a projection 56 on the back plate 51 of the brake lining 5 on the brake application side, such that the pressure-receiving element 304 acts only on the pressing contour 54 with a suitable flat pressure surface 307. This can also be achieved in that a corresponding recess 56a is provided in the back plate 51 on the inlet side, which recess does not contact the pressure face of the pressure piece (fig. 3), which is preferably otherwise flat.

It is also possible to provide a one-piece projection of the back plate 51 or to mount a separate element, such as an attachment plate (Aufsatzblech)55, as a projection on the back plate. The attachment plate 51 may be welded or otherwise secured to the back plate. Alternatively, however, it is also possible to form the one-piece shoulder as a projection 56 in the form of a projecting region on the back plate 51 (fig. 5a, 5 b).

Alternatively, a metal plate forming a shoulder (as a projection) may also be fixed to the pressure-receiving member (not shown).

It can be provided that the entire active surface is located on the side of the center axis M304 in the outlet direction.

However, it is also possible that the center axis M304 extends through the active surface and that the active surface has a greater extent towards the outlet side than towards the inlet side, and that the center of gravity and the effective center of gravity of the entire lining 5 and of the friction material 52 can continue to be oriented in the circumferential direction relative to the center axis M1 of the pressure piston 304 by a corresponding distribution of the recesses 55 and/or ribs 56 on the back plate 51.

The illustrated semi-circular contour or ring segment-like contour of the active surface is advantageous. Furthermore, it is advantageous if the entire active surface is located laterally to the center axis. This is preferred, but not mandatory.

The pressure-bearing part 306 can be of substantially cylindrical design on the end of the pressure piston 304, wherein the pressure surface 307 is therefore preferably planar. It may be centrally located.

The pressure piece 306 can also be of oval design, for example, and is mounted so as to be displaceable toward the outlet side or eccentrically on the end of the portion 305.

However, it is also possible for the center axis to extend through the active surface and for the active surface to have a greater extent towards the outlet side than towards the inlet side.

In the right-hand and left-hand disk brakes of the vehicle, the active surfaces, at which the pressure surface 304 and the seat surface 53 abut against one another when the disk brake applies the brake, are offset on the outlet side in the preferred direction of rotation relative to the brake disk 4 and in the circumferential direction of the center axis M of the piston 304, respectively.

In order to satisfy the conditions, according to one variant, the brake lining of the right-hand disc brake of the vehicle on the brake application side has a different back plate than the brake lining of the left-hand disc brake on the brake application side.

According to one variant, the disk brake 1 "on the right side of the vehicle" for the right end of the axle is constructed essentially exactly like the disk brake 1 "on the left side of the vehicle" for the left end of the axle (in particular the pad mounting groove of the brake carrier and the pressure piece of the brake application device), except for its two brake pads. However, it is also possible to differentiate the individual elements (e.g. plain bearing — fixed bearing and floating bearing) for the right-hand and left-hand disc brake, since, for example, if two fixed bearings are to be arranged "on the inlet side" on the disc brake, corresponding differences in this region occur on the left-hand disc brake and the right-hand disc brake.

In this case, the recesses 56a can be designed such that they are aligned, in particular completely aligned, when the back plates thereof are stacked congruent (fig. 6b, 6 c).

Thus, for example, in the case of a right-hand disc brake, the recess 56a of the brake application-side brake lining 5 is located in the back plate completely or predominantly, in the case of a brake application-side brake lining 5, on the right-hand side, for example, of the center axis, and in the case of a corresponding left-hand disc brake, in the case of a brake application-side brake lining 5 is located in the back plate completely or predominantly, in the case of a brake application-side brake lining 5, on the left-hand side, for example, of the center axis (fig. 6a, 6b, 6 c). It can therefore be advantageous to mark whether the brake lining is provided or designed for the left side or the right side of the vehicle, or the disk brake fitted thereto is provided or designed for the right side or the left side of the vehicle.

Fig. 6 illustrates this in a very intuitive way. Fig. 6a) therefore shows a perspective view of a brake lining 5L for the brake application side of a disc brake on the left side of a vehicle, wherein the circular surface shows the preferably planar pressure surface 307 of the pressure-bearing part acting on the back plate 51. Fig. 6 also shows in b) the brake lining 5L on the left side of the vehicle for the brake application side of the disc brake, without the pressure surface 307. Fig. 6c then shows the brake lining 5R on the right side of the vehicle for the brake application side of the disk brake, wherein the recess 56a or recess of the brake lining is located further to the left on the back plate 51 in the left-hand disk brake and further to the right on the back plate (with respect to the center of the back plate) in the right-hand disk brake, and the pressure piston 305 acts on the recess 56a or recess via a pressure piece 306 (see also fig. 5). Since the recess 56a is located completely or partially below the pressure surface in the back plate on the inlet side, the active surface is oriented eccentrically or not centrally in the circumferential direction with respect to the brake disk.

It is also to be noted that the brake linings 5, 6 can have a pressure spring 7 to which a cover 7a belongs, by means of which cover the pressure spring 7 can be fixed to the actual brake lining.

Reference numerals

1 disc brake

2 brake support

201 brake application side

202 reaction side

203 lining attaching groove on brake applying side

204 reaction side lining mounting groove

205. 206 transverse strut

207. 208 longitudinal strut

209. 210 entrance side bracket angle

211. 212 support angle on the exit side

213. 214 plain bearing

3 brake caliper

301 brake application side

302 reaction side

303 opening

304 pressure piston

305 cylindrical section 305

306 pressure-bearing piece

307 pressure surface

308 shoulder

4 brake disc

5. 6 brake lining

51. 61 backboard

52. 62 Friction material

53 seat surface

54 Rib

55 gap part and concave part

56 projection

56a recess

M5 center of gravity

M51 central axis

M304 central axis

Axis of rotation A4

And D, rotating direction.