DE102011002567A1 - Disk brake, particularly for motor vehicle, comprises brake holder which is firmly arranged at both sides of brake disk, where friction lining is firmly arranged on friction lining carrier in axial direction of brake disk - Google Patents

Abstract

The disk brake comprises a brake holder (2) which is firmly arranged at both sides of a brake disk. A friction lining (4) is firmly arranged on a friction lining carrier (3) in an axial direction of the brake disk. The friction lining carrier is supported at the brake holder by a supporting device (14). The support device is rotated around a rotational axis in an area (16). An independent claim is also included for a method for determining acting brake force.

Description

The invention relates to a disc brake according to the preamble of claim 1 and to a method for determining an acting braking force or an acting braking torque on a disc brake according to the preamble of claim 10.

A disk brake has, in a known design, a brake disc which is mounted on the hub of a wheel to be braked and to which friction linings in the form of brake pads or friction linings are pressed from both sides. These friction linings are mounted in a so-called caliper. The caliper is also referred to as a brake caliper and spans the brake disc. The activation of the brake is usually hydraulically by means of at least one brake piston as an actuator. In motor vehicles part disc brakes are usually used, ie disc brakes, which use only a portion of the surface of the disc as a friction surface.

Furthermore, in automobiles so-called floating caliper brakes are preferred. Floating caliper brakes have, in contrast to fixed caliper brakes, the actuators only on one side of the disc. The design of the floating caliper brake makes it possible to build the braking force on both sides of the brake caliper basically only one actuator. The longitudinally displaceably mounted or floating suspended caliper transfers the pressure applied by only one actuator mechanically to the other side of the brake disc. Floating caliper brakes require only relatively small space, so that a floating caliper brakes can be better placed at a lower height compared with fixed caliper brakes. Furthermore, floating caliper brakes have a high efficiency and are relatively simple in construction and maintenance. Thus, in particular friction or friction linings can be exchanged in a short time.

In known disc brakes serve as an actuator hydraulically operated pistons, which are displaceable by means of hydraulic pressure in corresponding actuators. In the case of an electromechanically actuated disc brake instead of a hydraulic cylinder, an electromechanical actuator is used. Likewise, pneumatic actuators are known.

For use in electric brake systems, it would be desirable, regardless of the exact structural embodiment of the disc brake, to detect a currently active braking force or a currently acting braking torque of the brake constantly and as accurately as possible. Only on this basis, the disc brake can be controlled reliably and with a required accuracy to comply with a user specified braking request and also to be able to report back to this and to perform slip-controlled braking (antilock braking).

From the prior art various approaches are known to determine the clamping force (normal force) of a disc brake, d. H. the force with which the friction linings are pressed in a direction normal to the brake disc surface (i.e., in the axial direction of the brake disc) against the brake disc. However, the application force is not proportional to the braking force (circumferential force) or the braking torque. Thus, one factor to consider is the coefficient of friction between the friction lining and the brake disk, which is dependent on conditions such as temperature, humidity and dirt and fluctuates during operation. The braking torque is proportional to the braking force with a so-called effective friction radius, which is also variable and can not be determined exactly. Accordingly, for a hydraulically actuated disc brake according to the current state of knowledge due to the high complexity of the processes, the course of the braking torque can not be reliably determined from the course of the brake pressure or the application force.

Approaches for determining the clamping force of a disc brake usually build on an elastic expansion of the caliper (in a direction perpendicular to the brake disc surface (axial direction)) on. Thus, it is known to measure the widening of the caliper with a strain gauge, which is glued in a yoke portion of the caliper, with which the brake caliper engages over the brake disc. Also in the DE 10 2006 029 978 B3 For example, a method and apparatus for measuring a normal force acting on a disc brake will be described. For this purpose, a device is provided on the caliper of the disc brake, which measures the normal force based on an elastic widening of the caliper during brake application by measuring a shearing motion of a portion of the disc brake during widening of the caliper.

The object of the invention is to provide a disc brake and a method by means of which a measure of the acting braking force (circumferential force) or the braking torque acting on a disc brake can be detected continuously, with inexpensive means and with sufficient accuracy during a braking operation.

This object is achieved by the disc brake according to claim 1 and the method according to claim 10.

The invention is based on the idea that support the Reibbelagträger a support device on the brake holder, which is at least partially rotatable. This makes it possible that the Reibbelagträger cause a braking, albeit very small, rotation or rotation (torsion) of the support device, which is a measure of the braking force or the effective braking torque.

In order to capture the acting braking torque as completely as possible, all the friction lining carriers of the disc brake are preferably supported together on the same support device or the same support devices on the brake holder.

Preferably, the supporting device is designed as a separate component from the brake holder and comprises a second region in which the supporting device is supported with respect to a rotation about the axis of rotation against the brake holder (eg by positive engagement). Alternatively, it is preferred that the supporting device is connected in the second area in a material-locking manner with the brake holder.

Preferably, the degree of rotation or torsion of the support device or a part of the support device is detected by means of a sensor device and based on the measurement signal of the sensor device, the braking force acting or the braking torque acting, z. In a processing logic.

The support device is preferably rotatably mounted in at least a first region on the brake holder about an axis of rotation in the substantially axial direction of the brake disk (ie in the direction of the application force), so that a tangential frictional force generated during braking via the friction lining carrier leads to a rotation or torsion of the support device leads.

Each of the friction lining carriers is preferably supported on one side on a supporting device rotatably mounted at least on one side. Thus, the braking torque determination can be done by means of a single sensor device per disc brake.

According to another embodiment of the invention, the Reibbelagträger a disc brake preferably supported on two sides of each one at least one side rotatably mounted support device. There are then particularly preferred per disc brake two sensor devices, one per support device, for detecting a rotation or rotation of the support device available.

According to one embodiment of the invention, the support device is rotatably mounted in a first region about an axis of rotation on the brake holder and rotatably connected in the second region with the brake holder, so that the support device is supported with respect to a rotation about the axis of rotation against the brake holder. In such a storage of the support device, a sensor device is preferably used, which detects a rotation (torsion) of the support device. Particularly preferably, the rotationally fixed connection is designed as a positive connection, since such can be produced inexpensively and stably.

The sensor device for detecting the torsion preferably comprises a transmitter arranged on the support device and a transducer, which cooperate particularly preferably according to a magnetic measuring principle, since they work without contact and can be used in harsh environmental conditions. Advantageously, the transmitter magnetoelastic properties and the transducer comprises a magnetic field sensitive sensor element.

According to another embodiment of the invention, the support device is rotatably mounted in a first region about an axis of rotation of the brake holder and comprises a radially to the axis of rotation extended support member, the Ab support device side facing away from the brake holder is supported. Particularly preferably, the support device comprises a third region in which it is also mounted rotatably about the rotational axis on the brake holder. For safe storage of the support device, the first and the third area are advantageously arranged on different sides of the brake disc.

In a support of the support device via a radially extended support element, it comes with a braking to a rotation of the supporting device, whereby the support member is deformed or bent. Therefore, a sensor device is preferably used by which a caused by the rotation of the support device deformation / bending of the support element is detected. The deformation is measured simply and inexpensively by means of a deformation-sensitive sensor element arranged on the support element. Particularly preferably, the deformation is measured by a strain gauge mounted on the support element.

The disc brake according to the invention can be designed both as a floating caliper disc brake or as a fixed caliper disc brake. Advantageously, one of the friction linings can be brought directly into engagement with the brake disc by an actuating unit and the other friction lining can be brought into engagement by the action of a reaction force applied by the caliper housing.

Preferably, the disc brake is formed hydraulically, pneumatically or electromechanically actuated.

According to a preferred. Embodiment of the method according to the invention caused by a braking force rotation or rotation of at least a portion of the supporting device achieved in that the supporting device is rotatably mounted in at least a first region about an axis of rotation on the brake holder, while in a second region with respect to a rotation about the Rotary axis is supported against the brake holder.

From the extent of the detected rotation or rotation, an effective braking force or an acting braking torque is determined according to a preferred embodiment of the method, wherein a predetermined bending stiffness or a predetermined torsional rigidity of the supporting device or a part of the supporting device is particularly preferred. The bending stiffness or torsional stiffness is advantageously stored in a processing logic or a brake control device together with data on the geometric dimensions of the support device / the support element, so that a direct calculation of the braking torque from the measured torsion / deformation is feasible.

The determined braking force or the determined braking torque is preferably used to carry out an electronic brake control of the disc brake.

According to one embodiment of the method according to the invention, a rotation (torsion) of a support device is measured, which is mounted rotatably in a first region about an axis of rotation on the brake holder and in a second region rotatably connected to the brake holder.

The degree of twisting (torsion) is preferably determined by means of a magnetic measuring method, since these work without contact. Advantageously, a magnetoelastic measurement method is performed.

According to another embodiment of the method according to the invention, a measurement of a deformation of a supporting element of the supporting device is performed, wherein the supporting element expands radially to the axis of rotation of the supporting device and is supported with the supporting device facing away from the brake holder, so that upon rotation of the supporting device, a deformation of the supporting element occurs.

Preferably, an electrical control of the disc brake is carried out on the basis of the determined braking force or the determined braking torque.

According to a preferred embodiment of the method according to the invention this is carried out in service braking operations and in electronically controlled braking, and thus serves to improve the comfort.

Further preferred embodiments will become apparent from the subclaims and the following description with reference to figures.

It show schematically

1 a known Faustsattel disc brake,

2 a detail of a first embodiment of a disc brake according to the invention,

3 two embodiment of a supporting device for a disc brake according to the invention, and

4 a detail of a second embodiment of a disc brake according to the invention.

1 schematically shows a saddle of a known caliper disc brake in an exploded view, which is a brake holder 2 and a caliper housing 1 includes. brake support 2 is over two mounting holes 6 on a motor vehicle, z. B. on the wheel of the motor vehicle, fastened. Caliper housing 1 engages with its saddle back unrepresented brake disc and two arranged on both sides of the brake disc friction linings 4 , each on a Reibbelagträger 3 are attached. In 1 For the sake of clarity, only one of the friction lining carriers is 3 (the outer friction pad). Caliper housing 1 is via suitable guide pins, which at the breakpoints 7 and 8th are attached, in a known per se axially (z-direction) slidably to the brake holder 2 stored. brake support 2 includes two pad guide rails 11 which engage over the brake disk and in each case two formations arranged on both sides of the brake disk (eg hammer head holder) 5 which engage for engagement with the friction lining carriers 3 arranged formations 9 (eg hammerheads) are executed.

In caliper housing 1 is on the inner brake disc side in the area 22 integrated an actuating unit, not shown, in order to apply a Bremszuspannkraft on the inner (not shown) friction lining can. In this case, the actuating unit preferably comprises a brake piston, which is hydraulically, electrically or electromechanically actuated. When the brake is actuated, initially a piston force acts on the inner friction lining 4 and presses it, after overcoming a clearance, against the brake disc. The inner friction lining 4 opposite outer friction lining 4 is in response to an operation of the inner friction lining 4 by axial displacement of the caliper housing 1 (in the z direction) also known to be pressed against the brake disc. On both sides of the brake disc, the same contact pressure / clamping force acts.

When braking is on each friction lining 4 a tangential friction force is effective (tangential to the brake disc surface, ie perpendicular to the axial direction (z) of the brake disc), through which the Reibbelagträger 3 from the brake disc is "taken" until Reibbelagträger 3 (depending on the geometric design of the formations 5 and 9 ) over one or both of the formations 9 to brake holder 2 supported. The support forces are fixed to the brake holder 2 attached hammer head holder 5 on brake holder 2 transfer. Depending on the geometric design of the individual formations 5 and 9 On the two sides can be a friction lining 3 initially on only one side of the brake holder 2 support, either by train or by pressure, or Reibbelagträger 3 can also be on both sides at the same time to brake holder 2 support.

In 2 a section of a first embodiment of a disc brake according to the invention is shown schematically. For better clarity is only a friction lining 3 as well as its support on the brake holder shown on one side. friction lining 3 with friction lining 4 rests on one side over a supporting device 14 to brake holder 2 starting in one area 16 rotatable on brake holder 2 is stored, for. B. by a plain bearing. For support on the brake holder 2 includes support device 14 a support element 12 extending radially outwards, ie perpendicular to the axis of rotation of the support device 14 , extends. The support device 14 opposite end of the support element 12 rests on brake holder 2 from. For example, this is the end of the support element 12 positive and non-positive between two pins 23 of the brake holder 2 arranged, whereby the end of the support element 12 is held stationary.

According to the example is support device 14 formed substantially cylindrical and with a groove 24 provided on which a Halterausformung 9 of the friction lining carrier 3 can intervene. According to the first embodiment is supporting device 14 additionally in area 16 ' rotatable on brake holder 2 stored, with area 16 and area 16 ' are arranged on both sides of the brake disc. groove 24 is in an area between the areas 16 and 16 ' arranged.

When braking with a transmitted to the brake disc braking torque M _B acts on friction lining 4 and thus on friction lining carrier 3 a tangential frictional force over the molding 9 of the friction lining carrier 3 on the support device 14 engages and a (very slight) rotation of both sides rotatable on the brake holder 2 mounted support device 14 causes. This rotation of the support device 14 leads, as the one end of the support element 12 on the brake holder 2 is held, to a bend of support element 12 , On support element 12 are z. B. strain gauges 15 attached, which capture the degree of bending. Based on the measured bending, taking into account the known stiffness of the support element 12 as well as the known geometric arrangement, are closed to the braking torque M _B.

In 3 two embodiments of a support device for a disc brake according to the invention are shown schematically.

In the 3a ) shown supporting device 14 corresponds essentially to the basis of 2 already described supporting device. Support device 14 comprises a cylindrical body with a groove 24 on which a Halterausformung 9 of the friction lining carrier 3 can intervene. Support device 14 is in a first area 16 rotatable about its cylinder axis (rotation axis) to brake holder 2 mounted and supported in a second region via a radially outwardly extending support element 12 with respect to a rotation about the cylinder axis to the brake holder 2 from. For measuring a bending of the support element 12 at the. Brakes are on support element 12 at least one deformation-sensitive sensor element 15 attached, z. B. in the form of a strain gauge.

This in 3b ) illustrated second embodiment of a supporting device 34 also includes a cylindrical body with a groove 24 on which a Halterausformung 9 of the friction lining carrier 3 can intervene. Support device 34 is in a first area 16 rotatable about its cylinder axis (rotation axis) to brake holder 2 stored, for. B. by a sliding bearing, and is supported in a second area 32 against rotation about the cylinder axis to the brake holder 2 from. For this purpose, supporting device 34 positive locking with brake holder 2 be connected, z. B. over a square shaping 35 (as in 3b ), which in a correspondingly formed recess in the brake holder 2 plugged or pressed in, or via a Torx connection. By the rotationally fixed attachment of the support device 34 in the second area 32 is a rotation of the Äibützvorrichtung (as in the example of the support device 14 described) prevented. Instead, when braking over the shaping leads 9 of the friction lining carrier 3 on the support device 34 attacking force to a torsion / rotation of the supporting device 34 , The degree of torsion is detected by a suitable sensor device, based on which then, for. B. taking into account the known torsional stiffness of the support device 34 , on the braking torque M _B can be closed. According to the in 3b ) illustrated embodiment, the sensor device comprises a on the support device 34 arranged transmitter 13 and a meter 10 , which work according to a magnetic measuring principle. For example, on the outrigger 34 a magnetoelastic structure 13 applied or integrated, which in their deformation as a result of the torsion of the support device 34 generates a magnetic field whose strength depends on the degree of rotation. The magnetic field strength is determined by magnetic field sensitive sensor element 10 , z. B. a Hall element, measured in the vicinity of the magnetoelastic structure 13 is arranged.

4 schematically shows a section of a second embodiment of a disc brake according to the invention. Here is a friction lining 3 shown, which is on one side via a supporting device 34 and on the other hand in a conventional manner, for example via a hammer head holder 5 , to brake holder 2 supported. Support device 34 is rotatable on one side to brake holder 2 stored (not shown) and is supported by a form-fitting square shaping 35 against rotation about its axis of rotation to the brake holder 2 whereas hammerhead holders 5 fixed with brake holder 2 is connected or designed in one piece with this.

To determine the effective braking torque is the braking at a support device 34 occurring torsion, which is measured by means of a suitable sensor device. For an accurate determination of the braking torque are the engaging portions of supporting device 34 (groove 24 ) / Friction lining 3 (formation 9 ) and brake holder 2 (Hammer head holder 5 ) / Friction lining 3 (formation 9 ) formed and dimensioned such that at a braking, z. B. in a desired measuring range of the braking torque, Reibbelagträger 3 initially exclusively on the support device 34 to brake holder 2 supported. The at braking on friction lining 3 acting tangential forces are so complete (friction loss between friction lining 3 and brake holder 2 neglected) as supporting forces on supporting device 34 effective and lead to a corresponding twisting of supporting device 34 which measure is detected by the sensor device. The support via hammer head holder 5 is z. B. only effective if very large braking forces occur and / or if there is a break in the support via support 34 should come.

Alternatively, the one-sided support device can also be used as described in FIG 2 and 3a Be explained explained (supporting device 14 ).

In any case, as described above, in a one-sided support via a at least one side rotatably mounted support device 14 . 34 (with appropriate design of the other, solid support 5 . 9 ) with a single sensor device per disc brake a braking torque determination can be performed. The second support point for safety reasons (for a fault) 5 . 9 of the friction lining carrier 3 is z. B. come only in case of damage to the brake (eg., Breakage of a hammer head holder) to the effectiveness. By the sensor device can break at the steady force supporting support point 14 . 34 easily recognized.

In 2 and 4 For reasons of better clarity, only one of the friction lining carriers is in each case 3 the disc brake shown. In order to fully capture the effective braking torque, the (two or more) friction lining carriers are supported 3 the disc brake advantageously together via the same support device 14 . 34 to brake holder 2 from. Thus, so to speak, the sum of the supporting forces is detected, which reflects the braking torque of the disc brake.

Because the friction linings 4 As well as the brake disc worn during operation, the absolute position of the support or suspension of the friction lining changes 3 on the support device 14 . 34 with the degree of wear. As the friction lining 3 slidably mounted on the support device (or the supporting devices, see the third embodiment) are, despite the mobility of the Reibbelagträger 3 When worn, the forces on the brake pads 4 or their friction lining carrier 3 measured together as a sum signal at one end of the pad back plate. The transmitted to the disc brake torque is detected at the brake pads or more precisely at the Reibbelagträger as force, said force via a supporting device and its storage in a torsion of the supporting device ( 34 ) or a bend of a part ( 12 ) of the supporting device ( 14 ) (caused by a rotation of the support device with at the same time firm support of the part of the support device) is implemented, which is measured.

According to a third, not shown embodiment of a disc brake according to the invention, the Reibbelagträger support 3 the disc brake on two sides, so on both hammer heads 9 , on in each case one at least one side rotatably mounted supporting device 14 . 34 from. There are then per disc brake two sensor devices, one per support device, available to detect the torsion or bending of the support devices. In order to simplify the measurement signal processing, the two supporting devices of a disc brake are advantageously carried out similar, ie z. B. according to the in 3a ) or in 3b ) illustrated embodiment.

Regardless of the specific design of the disc brake, the effect is achieved by means of at least one sensor device (eg in the form of a torsion of the supporting device (FIG. 34 ) or a bending of a supporting element of the supporting device ( 14 )) of the tangential supporting forces of two or more Reibbelagträger 3 on at least one supporting device 14 . 34 measured, with the Reibbelagträger 3 together on the at least one side of the brake holder 2 rotatably mounted support device 14 . 34 support. From a measure of the measured effect (torsion / bending) is concluded on the effective braking torque. This is possible because the mechanical sizes of the support mechanism and the wheel diameter are known. For example, the measurement signal of the sensor device (s) to a processing logic, for. B. in a control unit of the brake system, forwarded and in the processing logic is calculated from the / the measurement signal (s), taking into account the known stiffness and geometry of the support device, a braking torque.

In principle, a supporting device, which is mounted rotatably on at least one side of the brake holder, suitable for braking torque detection in the forward running direction as well as in the reverse direction of the disc brake. Only the type of suspension of Reibbelagträger 3 on both sides (ie the geometric design of the formations 5 and 9 and the support device 14 . 34 and associated formations 9 ) is to be interpreted such that a braking torque detection in the forward direction as well as the reverse direction is possible.

The method described above for determining the braking torque of a disc brake is used for. As the application in service braking operations and in electronically controlled braking and contributes to the improvement of comfort.

The disc brake can be designed both as a caliper brake or as a fixed caliper brake.

QUOTES INCLUDE IN THE DESCRIPTION

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Cited patent literature

• DE 102006029978 B3 [0007]

Claims (15)

Disc brake, in particular for a motor vehicle, with a fixed brake holder ( 2 ), on which both sides of a brake disc ( 10 ), on friction lining carriers ( 3 ) fixed friction linings ( 4 ) in the axial direction (z) of the brake disk ( 10 ) are mounted slidably limited, wherein the Reibbelagträger ( 3 ) via at least one supporting device ( 14 . 34 ) on the brake holder ( 2 ), and wherein the friction linings ( 4 ) at a braking on each side surface of the brake disc ( 10 ) are pressed, characterized in that the supporting device ( 14 . 34 ) in a first area ( 16 ) rotatable about an axis of rotation on the brake holder ( 2 ) is stored. Disc brake according to claim 1, characterized in that the supporting device ( 14 . 34 ) in a second area ( 12 . 32 ) with respect to a rotation about the axis of rotation against the brake holder ( 2 ) is supported. Disc brake according to claim 1 or 2, characterized in that the disc brake one, in particular at or in the vicinity of the supporting device ( 14 . 34 ), sensor device ( 10 . 13 ; 15 ) by means of which caused by a braking force rotation or rotation of at least a portion of the supporting device ( 14 . 34 ) is detected, and in particular that the sensor device is connected to a processing logic for determining an effective braking force or an effective braking torque (M _B ) based on a measurement signal of the sensor device. Disc brake according to claim 2 or 3, characterized in that the supporting device ( 34 ) in the second area ( 32 ), in particular by a positive connection, with the brake holder ( 2 ), and that in particular the sensor device is designed such that it causes a rotation of the supporting device ( 34 ) detected. Disc brake according to claim 4, characterized in that the sensor device has a transducer arranged on the support (( 13 ) and a transducer ( 10 ), whereby transducers ( 13 ) and transducers ( 10 ) cooperate in particular according to a magnetic measuring principle. Disc brake according to claim 2 or 3, characterized in that the supporting device ( 14 ) a radially extending to the axis of rotation support ( 12 ), of which the supporting device ( 14 ) facing away from the brake holder ( 2 . 23 ) is supported, and that in particular the sensor device on the support ( 12 ) arranged deformation-sensitive sensor element ( 15 ). Disc brake according to claim 6, characterized in that the supporting device ( 14 ) a third area ( 16 ' ) in which the supporting device ( 14 ) rotatable about the axis of rotation on the brake holder ( 2 ), in particular the first ( 16 ) And the third ( 16 ' ) Area on different sides of the brake disc ( 10 ) are arranged. Disc brake according to one of claims 1 to 7, characterized in that the Reibbelagträger ( 3 ) each have two or more support devices ( 14 . 34 ) on the brake holder ( 2 ), each of the support devices ( 14 . 34 ) in a first area ( 16 ) rotatable about an axis of rotation on the brake holder ( 2 ) is stored. Disc brake according to claim 8, characterized in that on each of the support devices ( 14 . 34 ) a sensor device for determining a caused by a braking force rotation or rotation of the respective supporting device ( 14 . 34 ) is arranged. Method for determining an acting braking force or an acting braking torque (M _B ) on a disc brake, in particular for a motor vehicle, with a fixed brake holder ( 2 ), on which both sides of a brake disc ( 10 ), on friction lining carriers ( 3 ) fixed friction linings ( 4 ) in the axial direction (z) of the brake disk ( 10 ) are mounted slidably limited, wherein the Reibbelagträger ( 3 ) via at least one supporting device ( 14 . 34 ) on the brake holder ( 2 ), characterized in that caused by a braking force rotation or rotation of the supporting device ( 14 . 34 ) or at least part of the supporting device ( 14 . 34 ), in particular which in at least a first area ( 16 ) rotatable about an axis of rotation on the brake holder ( 2 ) is stored and / or in particular which in a second area ( 12 . 32 ) with respect to a rotation about the axis of rotation against the brake holder ( 2 ) is supported, is detected. A method according to claim 10, characterized in that from the extent of the detected rotation or rotation, an acting braking force or an acting braking torque (M _B ) is determined, in particular a predetermined bending stiffness or a predetermined torsional stiffness of the supporting device ( 14 . 34 ) or part ( 12 ) of the supporting device is taken into account. A method according to claim 11, characterized in that an electronic control of Disc brake based on the determined braking force or the determined braking torque (M _B ) is performed. Method according to one of claims 10 to 12, characterized in that a rotation of a supporting device ( 34 ), which in a first area ( 16 ) rotatable about an axis of rotation on the brake holder ( 2 ) and in a second area ( 32 ), in particular by a positive connection, with the brake holder ( 2 ) connected is. A method according to claim 13, characterized in that the degree of rotation of the supporting device ( 34 ) is determined by means of a magnetic measuring method, in particular a magnetoelastic measuring method. Method according to one of claims 10 to 12, characterized in that a rotation of the supporting device ( 14 ) based on a measurement of a deformation of a supporting element ( 12 ) of the supporting device ( 14 ) is detected, which is radially to the axis of rotation of the supporting device ( 14 ) and with the support device ( 14 ) facing away from the brake holder ( 2 . 23 ) is supported.

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