WO2003056204A1

WO2003056204A1 - Self-reinforcing electromechanical partially lined disc brake with improved friction lining guidance

Info

Publication number: WO2003056204A1
Application number: PCT/EP2002/014781
Authority: WO
Inventors: Martin Schautt; Antonio Pascucci; Henry Hartmann
Original assignee: Estop Gmbh
Priority date: 2001-12-28
Filing date: 2002-12-27
Publication date: 2003-07-10
Also published as: DE10164317C1; EP1458988A1; AU2002367191A1

Abstract

The invention relates to a self-reinforcing electromechanical partially lined disc brake (10) comprising a rotatable brake disc (14), an electric actuator generating an actuating force, and a friction lining (18a) actuated by the electric actuator in order to enter in contact with one side of the brake disc (14). The electric actuator acts on the friction lining (18a) so as to place it at a wedge angle (α) via a square assembly (22). In order to improve guidance of the friction lining, the square assembly (22) is provided with a pressure plate (24) acting on the friction lining (18a) and a thrust bearing (26) interacting therewith. The pressure plate (24) is rotatable in the peripheral direction of the brake disc (14) relative to the thrust bearing (26). Several first tracks (28) extending in the peripheral direction of the brake disc (14) are disposed in the pressure plate (24), each first track (28) comprising a lowest point (P) and two ramps (30, 32) extending in opposite directions from said lowest point. A second track (34) built in analogy with the first track (28) is disposed in the thrust bearing (26) across from each first track (28) of the pressure plate (24). Each couple configured by a first track (28) and a second track (34) assigned thereto forms a seat for a rolling body arranged between the tracks (28, 34). At least the ramps (30) responsible for delivering the friction lining (18a) when the brake disc (14) rotating in the main direction of rotation brakes display a rising angle corresponding to the wedge angle (α).

Description

Self-energizing electromechanical partial brake disc brake with improved friction lining guidance

The invention relates to self-energizing electromechanical partial brake disc brakes, in particular for motor vehicles. In such disc brakes, an electric actuator applies an actuating force that applies the brake lining or friction linings to the rotating brake disk. A self-energizing device in the form of a wedge arrangement uses the kinetic energy contained in the rotating brake disc to further feed the friction linings, i.e. the friction linings are pressed against the brake disc with a force which is significantly higher than the actuator force and which is not applied by the electrical actuator. The basic principle of such a brake is known from German patent 198 19 564.

Applying the self-boosting principle to a conventional type of brake disc, e.g. on a floating caliper partial brake disc brake for motor vehicles, the use of a conventional wedge arrangement brings with it a number of disadvantages: While a conventional hydraulic friction lining actuation only moves the friction lining axially back and forth with respect to the brake disc, a conventional wedge arrangement not only shifts the friction lining as part of the infeed movement axially, but also tangential to the brake disc. The distance between the inner and outer edge of the brake disc must be chosen accordingly so that the friction lining still touches the brake disc with its entire brake lining surface (and does not protrude with a part of the friction lining surface over the outer edge of the brake disc) , which increases the size and weight of the brake.

However, such a larger brake disc area cannot be fully used, since, as already mentioned, due to the wedge arrangement, the friction path changes depending on the desired braking torque, so that when braking with a predetermined braking torque, only part of the area defined between the inner and the outer brake disc edge is in contact with the friction lining. The effective lever arm of the brake also changes during the tangential displacement of the friction lining, which makes it difficult to correctly record the braking torque. Furthermore, grooves in the brake disc surface can hinder the tangential displacement of the friction lining. It would be desirable to have an electromechanical partial brake disc brake that combines the principle of self-energizing by means of a wedge arrangement with the compact, well-proven type of disc brakes that have a caliper that spans the brake disc and in which the friction path does not change during braking. Brakes of this type are designed as fixed caliper brakes or as floating caliper brakes.

The invention has for its object to provide a partial brake disc brake that takes into account the previously specified request.

This object is achieved according to the invention with a self-energizing electromechanical partial brake disc brake which has the features specified in patent claim 1. The disk brake according to the invention, which is particularly suitable for use in motor vehicles, has a wedge arrangement with a wedge arrangement with a pressure plate acting directly on a friction lining and an abutment interacting with the pressure plate for self-amplification of the actuating force introduced into the brake. The abutment is fixed with respect to movements in a plane parallel to the brake disc, while the pressure plate can be displaced in the circumferential direction of the brake disc relative to the abutment. The movement of the pressure plate in the circumferential direction of the brake disk leads to the delivery of the brake. For this purpose, a plurality of first raceways extending in the circumferential direction of the brake disk are embedded in the pressure plate, each of which has a lowest point and two ramps extending in the circumferential direction of the brake disk opposite from this lowest point. In the abutment, opposite to each first raceway of the pressure plate, a second raceway is formed which is analogous to the first raceway. Each pair of a first raceway and an associated second raceway forms a receptacle for a rolling element which is arranged between every first raceway and every second raceway. Those ramps of each receptacle that are used for an infeed of the friction lining (the term "infeed" here means the movement of the friction lining towards the brake disc) when braking

Brake disc rotating in the main direction of rotation have a rise angle corresponding to the wedge angle α of a conventional wedge arrangement. The term “main direction of rotation” here means the direction of rotation of the brake disk in which the brake disk usually rotates. In a motor vehicle disc brake, for example, the main direction of rotation is the forward rotation because the forward drive corresponds to the most common driving state of a vehicle by far. The described arrangement of first and second raceways with rolling elements located between them causes a helical feed movement, ie the friction lining of the disc brake according to the invention does not move tangentially to the brake disc when braking, but in the circumferential direction of the brake disc, ie it follows the ring shape of the brake disc exactly. The friction path, ie an imaginary track that the friction lining would leave on the brake disc surface during the braking process, does not change in the brake according to the invention, regardless of how hard the brakes are applied. The design of a disc brake according to the invention can therefore be just as compact as that of a conventional fixed or floating caliper disc brake without a self-boosting device. If necessary in the

Grooves on the brake disc surface do not disturb the friction lining movement, since the friction lining surface is not moved transversely to the grooves. Due to the constant friction path, the effective lever arm always remains the same.

In the case of a linear wedge arrangement in which the pressure plate and abutment move linearly relative to one another, the wedge angle α is decisive for the degree of self-reinforcement. The wedge angle is the angle at which the interacting wedge surfaces of the pressure plate and abutment are arranged with respect to a plane (e.g. the brake disc surface) to which the force is to be transmitted. However, the disc brake according to the invention does not use a linear wedge arrangement, but rather one in which the pressure plate and the abutment are rotated helically against one another in order to advance the friction lining, i.e. to move towards the brake disc. The ramps mentioned, which are embedded in the pressure plate and the abutment, are consequently helical ramps for which the ratio ξ between the angle of rotation φ related to the axis of rotation of the brake disc and the infeed path x has a defined value. The relationship

ξ - - ^x φ should be chosen so that it corresponds to the wedge angle α known from the linear case. This requires knowledge of the effective brake disc radius r _eff . The effective brake disc radius r _we k is the radius at which an idealized friction force F _R must act at one point in order to generate the same friction torque M _R as the real friction force F _R that acts flat on the friction lining surface. The effective brake disc radius is calculated M \ r - μ - p _N - dA F _R \ μ - p _N - dA

A with r eff = effective brake disc radius F _R friction force

M _R = friction torque

A = friction lining surface μ = local coefficient of friction on the surface element considered p _N = local contact pressure on the surface element considered

R = radius of the surface element considered

The result is the ratio sich

X = - = r _M , _r , - tan α, φ which means that the path that the later point of application of the frictional force follows when it approaches the brake disc is inclined by the angle α with respect to the brake disc plane. For the sake of simplicity, we will always speak of the wedge angle α below, but it goes without saying that this means that the angle α

Brake disc surface inclined helical approach path of the force application point of the friction force according to the above explanations is meant.

The wedge angle can remain the same over the entire delivery path, but it can also change depending on the delivery path. In a preferred embodiment of the disc brake according to the invention, the wedge angle α decreases with increasing feed path. In this way, in extreme situations, i.e. with a minimum coefficient of friction and a very high required friction or braking torque, the level of self-amplification increases without the brake getting stuck in normal situations due to an excessively high degree of self-amplification.

The ramps responsible for delivering the friction lining when braking a brake disk rotating counter to the main direction of rotation can have the same wedge angle α as those already mentioned, for delivering the friction lining when braking the brake disk rotating in the main direction of rotation. ramps. However, it can be advantageous to design the first-mentioned ramps with an angle of inclination that differs from the wedge angle of the latter-mentioned ramps, for example steeper, in order to reduce the pedal travel required for actuation. The lower degree of self-amplification at a larger wedge angle can be tolerated, since the braking torque required for braking the brake disk rotating counter to the main direction of rotation is usually significantly lower.

In principle, any type of rolling element is suitable for use in the disc brake according to the invention. According to one embodiment, the rolling elements are balls. The raceways in the pressure plate and the abutment have an at least approximately semicircular cross section, so that the ball rolling in the raceway touches the raceway in a linear manner and not only in a punctiform manner.

According to another embodiment, the rolling elements are cylindrical rollers. In this embodiment, two cylindrical rollers are preferably arranged next to one another along a common cylindrical roller axis in each rolling element receptacle. The rolling behavior of two short cylindrical rollers arranged side by side is significantly more favorable than the rolling behavior of a continuous cylindrical roller of corresponding length, since the difference in the rolling radii between the radially inner and the radially outer end of a short cylindrical roller is smaller. The proportion of sliding friction is thereby reduced, rolling friction predominates.

In order to ensure a synchronous movement of the rolling elements, they can be guided by means of a cage. Furthermore, springs or similar means can be provided which ensure permanent contact between the rolling elements (regardless of their shape) and the raceways. In embodiments in which two cylindrical rollers are arranged alongside one another along a common cylindrical roller axis, the radial guidance of the two cylindrical rollers is preferably carried out on the outside by a collar of the pressure plate that laterally delimits the first raceway and on the inside by a web that is between the two cylindrical rollers is arranged and extends from the abutment into the rolling element receptacle.

In order to achieve an exact dosage of the desired braking effect, at least one friction lining is actuated directly in the brake according to the invention as already mentioned. For this purpose, preferred embodiments of the invention Disc brake an electric actuator with two electric motors, the rotary movement of which is transmitted to the pushing plate of the pressure plate in the circumferential direction of the brake disc via a spindle drive on the pressure plate. An electric motor is arranged on one side of the pressure plate and the other electric motor on the opposite side of the pressure plate. An electrical actuator designed in this way enables the pressure plate to be positioned without play, regardless of whether the wedge arrangement is currently acting as a tension wedge or as a pressure wedge.

In preferred embodiments of the disk brake according to the invention, the abutment is supported on a brake caliper which overlaps the brake disk and which, during a braking operation, presses another friction lining against the other side of the brake disk (floating caliper principle). The abutment can be moved to and from the brake disc with the brake caliper.

According to a preferred embodiment, which can be used with floating caliper and fixed caliper brakes, at least the ramps responsible for delivering the friction lining when the brake disc rotating in the main direction of rotation is braked are shaped such that during the infeed process, i.e. when the friction lining moves towards the brake disc surface, the pressure plate not only moves towards the brake disc, but is also tilted relative to the brake disc surface. In this way, a misalignment of the friction lining caused by an expansion of the brake caliper is counteracted, and it can be ensured that the friction lining surface always comes into contact with the brake disk surface in exactly parallel fashion. An uneven distribution of the contact pressure and an uneven wear of the friction lining is avoided.

The degree of tilting of the pressure plate described above preferably increases with increasing angle of rotation between the pressure plate and the abutment, in order in this way to compensate for the widening of the brake caliper which increases with increasing braking torque.

Two preferred exemplary embodiments of an electromechanical partial brake disc brake with self-amplification are explained in more detail below with reference to the attached schematic figures. It shows: 1 is an overall view of an electromechanical partial brake disc brake in a spatial representation obliquely from above,

2 is a view similar to FIG. 1 with the brake caliper and abutment removed,

3 shows a view of the brake from FIG. 1 in a spatial representation obliquely from below with the pressure plate hidden,

4 shows the view from FIG. 1 with the brake in the braking position for a brake disk rotating in the main direction of rotation,

5 shows the view from FIG. 1 with the brake in the braking position for a brake disk rotating counter to the main direction of rotation,

6a-6c detailed views of the wedge arrangement with the brake released (FIG. 6a), braking in the main direction of rotation (FIG. 6b), and braking against the main direction of rotation (FIG. 6c),

Fig. 7a - 7c views corresponding to Fig. 6a to 6c for a modified, second embodiment, and

Fig. 8 section VIII - VIII of Fig. 7a.

Fig. 1 shows schematically an electromechanical generally designated 10

Part floating disc brake for a motor vehicle. The housing 12 of the brake 10 is shown in broken lines in FIG. 1 in order to allow a view of the components arranged in the housing 12. The housing 12 is provided for attachment to a component fixed to the vehicle, for example for attachment to a steering knuckle (not shown).

The brake 10 is assigned a brake disc 14 which is rotatable about an axis A and which is connected in a rotationally fixed manner to a component to be braked, for example to a vehicle wheel (not shown).

A floating caliper 16 is slidably guided on the housing 12 of the brake 10 parallel to the axis of rotation A of the brake disc 14. The floating caliper 16 engages over the brake disc 14 and acts with each of its two arms 16a and 16b on a brake pad 18 and 20. Each brake pad 18, 20 consists of a friction lining 18a, 20a and a carrier plate on which the friction lining 18a, 20a is fastened, for example by gluing. Only the carrier plate 20b is shown in the figures. While the vehicle-external brake pad 20 is actuated directly by the arm 16b of the floating caliper 16, a wedge arrangement 22 is present between the vehicle-internal brake pad 18 and the associated arm 16a of the floating caliper 16, which serves to self-amplify the actuating force introduced into the brake 10.

The most important components of the wedge arrangement 22 are a pressure plate 24, which acts directly on the brake pad 18, and an abutment 26, on one side of which the arm 16a of the floating caliper 16 acts and on the opposite side of which the pressure plate 24 is supported. Both the pressure plate 24 and the abutment 26 have a circular segment shape. The pressure plate 24 can also be directly connected to the friction lining 18a, for example by gluing, and thus also take over the function of the carrier plate.

As can be seen from FIG. 2, a plurality of first raceways 28, which each have a deepest point P and two ramps 30, 32 extending in opposite directions, are embedded in the surface of the pressure plate 24 facing the abutment 26 include. In the exemplary embodiment shown, four first raceways 28 are present, but more or fewer first raceways 28 may be present in the case of modified exemplary embodiments which are not shown.

From Fig. 3 it can be seen that in the surface of the ^¬ abutment 26 facing the pressure plate 24, second raceways 34, which are designed analogously to the first raceways 28, are let in at locations which lie opposite the first raceways 28. Each pair of a first raceway 28 and an associated second raceway 34 forms a receptacle for a rolling element, which is arranged between each first raceway 28 and every second raceway 34 and rolls or rolls in the receptacles formed by the raceways 28, 34 can pass on.

In the exemplary embodiment shown in FIGS. 1 to 6, the rolling elements are balls 36. The profile of the raceways 28 and 34 is adapted to the rolling elements used, ie the raceways 28 and 34 of the first exemplary embodiment shown in FIGS. 1 to 6 have one of the balls 36 adjusted cross sectional contour. The contact of each ball 36 in the raceways 28, 34 is thus linear and not only punctiform, which improves the guidance of the balls 36 and reduces the material load occurring in the receptacles.

The figures show four recordings, each with one arranged therein

Ball 36. At least three recordings with a ball are required for geometrically determined guidance. However, clearly more than four balls can be used (in corresponding images), and the number of balls can be even or odd. The general rule is that more balls equalize the load on the wedge arrangement 22 and increase the load capacity of the wedge arrangement as a whole. Each ball 36 represents a force application point, and many force application points reduce the internal stiffness requirement of the pressure plate 24 and abutment 26 so that these parts can be made easier.

An electric actuator, which in the exemplary embodiment shown is formed by two linear actuators 38, 40, serves to actuate the disc brake 10. Each linear actuator 38, 40 has an electric motor 42, 42 'with an integrated spindle nut and a rotation angle sensor and a push rod 44, 44' designed as a spindle. Ball joints 46, 46 'and 48, 48' couple the linear actuators 38, 40 on the one hand to the housing 12 of the brake 10 and on the other hand to the pressure plate 24. By actuating the two electric motors 42, 42 ', the pressure plate 24 can be moved back and forth along a circular path following the brake disc 14.

The structure described, consisting of pressure plate 24, abutment 26 and receptacles arranged therebetween with balls 36 therein, forms a ball ramp arrangement for self-reinforcing the actuating force introduced into the brake, in which the pressure plate 24 can be rotated in the angular direction φ relative to the abutment 26. The raceways 28, 34 are designed so that for the path of the center of gravity of the inner friction lining 18a between the movement component tangential to the brake disc and the movement component in the feed direction x, which is parallel to the axis of rotation A, there is a ratio of tanα, where α is the for self-energizing brakes is typical wedge angle α.

The function of the disc brake 10 will now be explained in more detail with reference to FIGS. 4 to 6. To actuate the brake, the pressure plate 24 is displaced in the direction of rotation of the brake disc 14 by means of the two linear actuators 38, 40. The balls 36 run from their starting positions shown in FIG. 6a, in which they rest at the lowest point P of each raceway 28, 34, up the ramps 30 (see FIG. 6b), as a result of which the pressure plate 24 and with it the brake pad 18 are moved in the direction of rotation of the brake disk 14 and at the same time in the direction x toward the brake disk surface (delivery phase).

As soon as the friction lining 18a comes into contact with the brake disc 14, a reaction force arises which is transmitted to the floating caliper 16 via the pressure plate 24 and the abutment 26. In a known manner and therefore not further explained here, the floating caliper 16 then shifts relative to the housing 12 of the brake 10, as a result of which the friction lining 20a of the brake pad 20 also comes into contact with the brake disc 14.

In the further course of the braking process, the wedge arrangement 22 ensures that part of the kinetic energy contained in the rotating brake disc 14 is converted into a feed force that is normal to the surface of the brake disc, so that the two linear actuators 38, 40 only a small part of that required Braking torque required delivery force must apply. 4 shows the brake 10 in the applied state for braking a brake disk 14 rotating in the main direction of rotation. The friction linings 18a, 20a face each other exactly in this tightened state, while in the released state (see FIG. 1) they have an angular offset to one another.

The actuation of the linear actuators 38, 40 is carried out by an electronic control unit (not shown), which compares a friction force measured by a sensor (not shown) with a predetermined friction force setpoint and any

Corrects deviations. The control positions the pressure plate 24 by means of the two linear actuators 38, 40 in such a way that the desired frictional force is maintained even when the coefficient of friction fluctuates. The two linear actuators 38, 40, which can be controlled independently of one another, enable the pressure plate 24 to be positioned without play: at low required actuation forces, ie in areas in which the coefficient of friction μ corresponds to the tanα, the two linear actuators 38, 40 act against one another and thus eliminate any play. If larger actuation forces are required, which is the case if the value of the friction coefficient μ deviates strongly from tanα, one of the linear actuators 38, 40 is reversed so that the actuation forces of both actuators 38, 40 add up. If a brake disk 14 rotating counter to the main direction of rotation is to be braked, the linear actuators 38, 40 move the pressure plate 24 again in the direction of rotation of the brake disk 14, but now in the opposite direction to the previously described braking (see FIG. 6c). The balls 36 move up the ramps 32, which may have the same or a different pitch angle as the ramps 30. 5 shows the brake 10 in the locked position when the brake disk 14 rotating counter to the main direction of rotation is braked.

An adjusting device, generally designated 50 and not further explained, can move the abutment 26 parallel to the axis of rotation A of the brake disc 14 in order to compensate for the friction lining wear that occurs during operation of the brake 10.

FIGS. 7 and 8 show a second exemplary embodiment of the wedge arrangement 22, in which instead of balls 36 cylindrical rollers are used, which are arranged in appropriately adapted receptacles. As the section VIII-VIII from FIG. 7a shown in FIG. 8 shows, two cylindrical rollers 52, 54 are arranged alongside one another along a common cylindrical roller axis Z in each receptacle formed from a first raceway 28 'and a second raceway 34'. The radial guidance of the two cylindrical rollers 52, 54 takes place on the outside thereof by a respective collar 56, 58 laterally delimiting the first raceway 28 ', which in the exemplary embodiment shown is formed in one piece with the pressure plate 24, and on the inside by a web 60 which is formed on the abutment 26 in the second raceway 34 'and extends into the receptacle between the two cylindrical rollers 52, 54 (see FIG. 8).

The function of the wedge arrangement 23 according to the second embodiment corresponds to the function illustrated in Fig. 6, i.e. for braking a brake disk 14 rotating in the main direction of rotation, the cylindrical rollers 52, 54 run up the ramps 30 'from their starting position shown in FIG. 7a (see FIG. 7b), while for braking a brake disk 14 rotating in the opposite direction of rotation, the ramps 32 'can be used (see Fig. 7c).

In both of the illustrated exemplary embodiments, the ramps 30 in particular can be shaped such that the pressure plate 24 not only moves toward the brake disk 14 during the infeed process, but is also tilted relative to the brake disk plane. With such a configuration, the misalignment of the friction lining 18a caused by an expansion of the brake caliper 16 at high application forces can be achieved are counteracted, ie the friction lining surface is always kept parallel to the brake disc surface. Preferably, the degree of tilting of the pressure plate 24 increases with an increasing angle of rotation between the pressure plate 24 and the abutment 26, in order in this way to take into account a widening of the brake caliper 16 that increases with the application force.

Claims

claims

1. Self-energizing electromechanical partial brake disc brake (10), with

- a rotatable brake disc (14),

an electric actuator generating an actuating force,

- A friction lining (18a) actuated by the electric actuator for coming into contact with one side of the brake disc (14), on which the electric actuator acts to feed the friction lining (18a) via a wedge arrangement (22) with a wedge angle (α), characterized that

the wedge arrangement (22) has a pressure plate (24) acting on the friction lining (18a) and an abutment (26) cooperating therewith, the pressure plate (24) being rotatable in the circumferential direction of the brake disc (14) relative to the abutment (26),

- A plurality of first raceways (28) extending in the circumferential direction of the brake disc (14) are embedded in the pressure plate (24), each first raceway (28) having a lowest point (P) and two from this lowest point in opposite directions extending ramps (30, 32),

- In the abutment (26) opposite to each first raceway (28) of the pressure plate (24), a second raceway (34) formed analogously to the first raceway (28) is let in,

- Each pair of a first raceway (28) and an associated second raceway (34) forms a receptacle for a rolling element between each first raceway

(28) and every second track (34) is arranged, and

- At least the ramps (30) responsible for delivering the friction lining (18a) when the brake disk (14) rotating in the main direction of rotation is braked have a rise angle corresponding to the wedge angle (α).

2. Disc brake according to claim 1, characterized in that the wedge angle (α) changes over the feed path.

3. Disc brake according to claim 2, characterized in that the wedge angle (α) decreases with increasing feed path.

4. Disc brake according to one of claims 1 to 3, characterized in that the ramps (32) responsible for adjusting the friction lining (18a) during braking of the brake disc (14) rotating counter to the main direction of rotation have a different rise angle from the wedge angle (α) exhibit.

5. Disc brake according to one of the preceding claims, characterized in that the rolling bodies are balls (36).

6. Disc brake according to one of claims 1 to 4, characterized in that the rolling elements are cylindrical rollers.

7. Disc brake according to claim 6, characterized in that in each rolling element holder two cylindrical rollers (52, 54) are arranged alongside one another along a common cylindrical roller axis.

8. Disc brake according to claim 7, characterized in that the radial guidance of the two cylindrical rollers (52, 54) on their outside by in each case a laterally limiting first race (28) collar (56, 58) of the pressure plate (24) and on it Inside by a web (60), which is arranged between the two cylindrical rollers (52, 54) and extends from the abutment (26) into the rolling element receptacle.

9. Disc brake according to one of the preceding claims, characterized in that the electric actuator comprises two electric motors (42, -42 '), the rotational movement of which to push the pressure plate (24) back and forth in the circumferential direction of the brake disc (14) via a spindle drive on the Pressure plate (24) is transmitted, an electric motor (42) being arranged on one side of the pressure plate (24) and the other electric motor (42 ') on the opposite side of the pressure plate (24).

10. Disc brake according to one of the preceding claims, characterized in that the abutment (26) is supported on a brake disc (14) overlapping brake caliper (16) which, during a braking operation, has a further friction lining (20a) against the other side of the brake disc ( 14) presses.

11. Disc brake according to claim 10, characterized in that at least the ramps (30) responsible for adjusting the friction lining (18a) when braking the brake disc (14) rotating in the main direction of rotation are shaped such that the pressure plate (24) during the infeed process. is not only moved towards the brake disc (14), but is also tilted relative to the brake disc plane in order to counteract a misalignment of the friction lining (18a) caused by an expansion of the brake caliper (16).

12. Disc brake according to claim 11, characterized in that the degree of tilting of the pressure plate (24) increases with increasing angle of rotation (φ) between the pressure plate (24) and the abutment (26).