DE102016116969A1 - Brake pad and disc brake with such a brake pad - Google Patents

Abstract

The present invention relates to a brake lining (9) for a disc brake (1) of a vehicle, comprising a lining carrier (14) and a friction lining (15) arranged thereon, which together have a thickness D, wherein between the lining carrier (14) and the friction lining (15) at least one adjusting means (11) is arranged, by means of which the friction lining (15) relative to the lining carrier (14) is relatively movable, wherein the relative movement of the lining carrier (14) to a change in distance between the latter and the friction lining (15) and a change in the thickness D leads.

Description

The invention relates to a brake pad for a disc brake for a vehicle according to the preamble of the independent claims 1 or 2 as well as a disc brake for a vehicle according to the preamble of claim 19.

Disk brakes of the generic type have a caliper with a brake application unit, preferably a brake carrier for mounting the brake caliper and brake pads, which are arranged on both sides of a brake disc. The force required for braking force is generated by the pressing of the brake pads by means of the application device, which provides for a plant of the pads on the brake disc. For this purpose, the brake pads must be moved in the axial direction of the brake disc. This shift process can be divided into two phases. In the first phase, the brake pads are moved with little force within the so-called clearance and finally brought into contact with the brake disc.

In the following second phase, the structure of the contact pressure between the brake pads and the brake disc takes place. For this purpose, it is necessary to move the brake pads according to the respective elasticity of the brake pads, the brake disc and the caliper. The distance traveled here by the brake pads displacement depends essentially on the height of the contact pressure. For strong braking operations, therefore, the two brake pads must be moved relatively far to produce a high contact pressure.

If the disc brake is released again, the brake pads are first pushed back by the stored due to the elastic deformation in this force. In the further consequence, the pressure pistons of the application device are actively withdrawn by a return mechanism of the disc brake. However, as a rule, the brake pads are not firmly connected to the pressure piston, there is the problem that the brake pads with low contact pressure can adhere to the brake disc. This applies in particular for the saddle-back side or reaction-side arranged brake lining of a sliding or floating caliper. In this frequently occurring type of calipers, only the inner, piston-side or application-side brake pad is pressed by the pressure piston to the brake disc. The outer reaction-side brake pad, however, is pressed by the reaction force, which results from the displacement of the caliper, to the brake disc.

When releasing the brake, there is now the problem that in particular the reaction-side brake pad, in the non-actuated state of the disc brake, is still pressed by the frictional forces of the brake caliper bearing with little force to the brake disc.

Brake pads that are still in contact with the brake disc when the brake is not applied cause residual grinding torques on the wheel brakes. The consequences of this are unnecessary wear of the brake pad and thus an additional burden on the environment due to brake pad wear and increased fuel consumption of the vehicle, since the residual grinding torques at the wheel brakes must be overcome by the drive motor of the vehicle.

The DE 10 2012 006 135 A1 describes a generic brake pad and a disc brake of the type mentioned. In order to achieve an active provision of the reaction-side brake pad, the pad carrier on its Bremsträgerhörnern elastomeric components, which experience an additional elastic deformation during the Anpressvorganges. The energy stored in the elastomer components due to the deformation work causes a restoring force opposite the application device when the brake is released. By this force exerted by the elastomeric components on the brake lining restoring force of the brake pad is actively released after retraction of the application device in its non-braking position of the brake disc.

In practice, it has been found that the known systems do not meet the requirements for different braking situations, brakes with low or high braking force. In particular, the elastomer components arranged on the brake carrier horns of the lining carrier are subject to high wear. In addition, it can over time lead to a change in the spring characteristic of the elastomer components, so that the restoring forces are no longer sufficient, in particular to completely space the reaction-side brake pad of the brake disc.

Thus, the present invention has for its object to provide a brake pad and a disc brake for a vehicle, with which the above-mentioned disadvantages can be overcome, in particular unnecessary wear of the brake pads by accidental contact of the brake pads, in particular the reaction-side brake pad on the brake disc in Non-braking condition of the disc brake to avoid.

This object is achieved by a brake pad for a vehicle with the features of claim 1 or 2 and by a disc brake with the features of claim 19.

In the brake lining according to the invention according to the independent claim 1 at least one (mechanical) adjusting means is arranged between the lining carrier and the friction lining relative to the lining carrier is relatively movable, wherein the relative movement of the lining carrier leads to a change in distance between this and the friction lining. The distance change between the lining carrier and the friction lining which can be achieved by means of the adjusting means is designed in such a way and thus results in the brake lining having a smaller thickness in its non-braking state than in its braking state. The term "thickness of the brake lining" is understood to mean the addition of the respective component and material thickness of lining carrier and friction lining in the axial direction (with respect to the brake disk axis of rotation) of the brake lining. Thus, it is possible to ensure a constant distance between the brake lining, that is to say between the friction lining on the lining carrier, and the brake disk in the non-braking state, whereby contact of the friction lining with the brake disk and the residual grinding moments associated with it are reliably avoided. Another advantage of this embodiment is that the brake lining forms a closed functional unit. Thus, such a trained brake pad is not affected in its performance by the execution of the caliper interface of the caliper. The friction lining preferably has a covering material and a base plate. The adjusting means is then arranged between the base plate and the lining carrier plate.

In the brake lining according to the invention according to claim 2 at least one adjusting means is arranged on the brake lining, by means of which an axial distance between the caliper and the friction lining of the brake pad is variable. The achievable by means of the adjusting distance change between the caliper and the friction lining - here is not meant the elastic change in thickness of the brake pad as a result of the actual braking force, which occurs limited in a brake pad without additional adjustment means - causes the friction lining in the non-braking state of the disc brake a smaller Distance to the caliper, as in the braking state of the disc brake. In this way, an exemption of the brake pad can be set between the reaction-side brake pad and the brake disc in the non-braking state, whereby a contact between the friction lining of the reaction-side brake pad and the brake disc is avoided. The occurrence of residual grinding torque in the non-braking state and the associated consequences are avoided.

The brake pads according to the invention according to the independent claims 1 and 2, the idea is common to convert the brake pad back to a non-braking position by a distance variation between the friction lining of the reaction-side brake pad and the caliper after releasing the disc brake, in a contact of the friction lining with the brake disc and the associated residual grinding moments are reliably avoided.

Preferably, the brake pad may be relatively limited (e.g., up to a few millimeters, e.g., up to a lateral stop) relative to the caliper in the tangential direction. In this case, it is possible to use the circumstance that when the braking process is initiated, first the brake lining arranged on the application side is brought into contact with the brake disk by displacement of the same or by displacement of the brake caliper with little force. Due to the rotational movement of the brake disc occurs between the friction lining and the brake disc acting in a tangential direction friction force. This frictional force can cause a relative movement between the reaction-side brake pad and the caliper, which in turn leads by means of the at least one adjusting means to a change in distance between the brake pad and the caliper. In order to limit the relative movement directed in the tangential direction, a stop is integrated in the caliper, which causes a limitation of the displacement path.

In particular, the reaction-side friction lining can be relatively movable with respect to the lining carrier in the tangential direction. In this case, it is possible to use the fact that, when the braking process is initiated, the brake lining arranged on the reaction side is first brought into contact with the brake disk with little force from the brake disk. Due to the generally present when initiating a braking operation (when driving) rotational movement of the brake disc, then occurs between the friction lining and the brake disc acting in a tangential direction friction force. This frictional force can cause a relative movement between the lining carrier and the friction lining of the brake pad, which in turn leads to a change in distance between the lining carrier and the friction lining. The thickness of the brake pad thus changes depending on the operating situation of the disc brake.

In a preferred embodiment of the invention it can be provided that the at least one adjustment means is adapted to generate a linearly extending relative movement. In this case, the relative movement can follow a ramp-shaped course. This can be achieved in that the at least one adjusting means has a ramp-shaped contour. By means of the ramp shape, the change in distance between the Brake pad and caliper vary. One or more ramped contours designed as inclined planes can be provided.

In particular, the at least one adjusting means can be designed as two wedge-shaped sliding surfaces arranged opposite one another. Such sliding surfaces are structurally easy to implement.

In this case, at least one sliding surface may be arranged on the caliper and on the brake lining. The arrangement of the sliding surface on the brake pad takes place on the side facing away from the friction lining of the brake pad.

According to an alternative embodiment of the at least one adjusting means can be provided that in the lining carrier and the friction lining are arranged in pairs opposing recesses, which serve to receive trained as adjusting rolling elements. The use of rolling elements as adjusting means has the advantage that the friction between the lining carrier and the friction lining is lower. The rolling elements may be spherical or have a circular cylindrical cross-section.

It is advantageous if the rolling elements are comprised in sections by a guide element extending substantially flatly between the lining carrier and the friction lining. The guide element secures the rolling elements against unintentional slipping out of the recesses in the lining carrier and friction lining. This can prevent tilting.

The recesses should have a contour substantially adapted to the rolling elements.

Furthermore, the recesses may have an edge region with a constant or a variable pitch. By means of the slope in the edge region of the respective recess, the response of the brake lining can be influenced when the relative movement occurs.

In a preferred embodiment of the invention it can be provided that the at least one adjusting means is adapted to generate a non-linear relative movement. In this case, a movement of the brake pad in the tangential direction can lead to a sudden movement in the axial direction of the brake pad. This makes it possible to achieve a fast response of the reaction-side brake pad when initiating the braking process.

For this purpose, the at least one adjusting means can be embodied as at least one element pivotable about a tilt axis, which engages with its ends in corresponding recesses arranged on the lining carrier and the friction lining. The pivotable element preferably has a slot-shaped cross-section. The arrangement between the lining carrier and the friction lining takes place transversely to the longitudinal axis of the brake pad. In this case, the pivotable elements extend in sections across the width of the brake pad.

It is advantageous if the at least one pivotable element is associated with a resilient return element. The tilting of the at least one pivotable element leads to a deformation of the resilient return element. This deformation work is abruptly released in the process of releasing the brake, so that the return of the at least one pivotable element to its initial position in the non-braking state of the brake pad also expires accelerated.

In particular, the lining carrier and the friction lining may be connected to each other at their free ends by clip-like spring elements. These allow a shift of the lining carrier and the friction lining in the tangential direction and at the same time ensure that the two components of the brake lining can not separate from each other. The adjustment can be limited by a provided in the lining carrier stop contour. By this stop contour, the zurücklegbare adjustment can specify in the tangential direction.

The disc brake according to the invention for a vehicle according to claim 19 is characterized in that the moving through the sliding caliper brake pad according to one of claims 1 to 18 is formed.

It is advantageous if the reaction-side brake pad and the caliper are tangentially and axially limited relative to each other displaceable.

Preferably, then at least one adjusting means is associated with the brake caliper and the reaction-side brake pad, by means of which an axial relative position between the caliper and the friction lining of the reaction-side brake pad is changeable. This makes it easy to use advantages described above on the pad in the disc brake easy.

Structurally, it is simple if the at least one adjusting means has two wedge-shaped sliding surfaces arranged opposite one another. It is then further advantageous if at least ever a sliding surface are formed on the caliper and on the lining carrier.

In addition, it is advantageous if the reaction-side brake lining is associated with a return spring fixed to it, which is also fixed to the brake caliper.

A preferred embodiment of the disc brake provides that a Abstützkontur is integrated into the caliper, which limits the relative movement of the friction lining against the lining carrier in the tangential direction.

In particular, the application device can be integrated with an elastic component, by which the pressure piston can be reset against an actuation force of the application device. While in a pneumatically actuated brake, a displacement of the application-side brake pad in the direction of the brake disc due to the compressibility of the pressure medium used, in particular air, as a rule, it is preferably required in a hydraulically actuated brake an additional force, which is opposite to the actuating force. Here, the elastic member may be designed as a compression spring or other component. With a force-displacement behavior adapted to the actuating force, a limited return of the application device or of the pressure piston can be achieved. Embodiments of the invention will be described below with reference to the accompanying drawings.

Show it:

1 a schematic view of a disc brake with a brake pad according to the invention according to a first embodiment in the non-braking state;

2 a schematic view of the disc brake according to 1 with pressure piston side shifted brake pad at the beginning of a braking operation;

3 a schematic view of the disc brake according to 2 with brake pad resting on the brake disc on the saddle side;

4 a schematic view of the disc brake according to 3 with in the direction of rotation of the brake disc relative to the lining carrier moving friction lining;

5 a schematic view of the disc brake according to 4 when releasing the disc brake;

6 a schematic view of the disc brake according to 5 after completion of the braking process;

7 a perspective view of a brake pad according to a second embodiment;

8th a longitudinal sectional view of the brake pad according to 7 in the non-braking condition;

9 a detailed view VIII of the brake pad according to 8th in the non-braking condition;

10 the detailed view VIII of the brake pad according to 9 in braking condition;

11 a perspective view of a brake pad according to a third embodiment;

12 a longitudinal sectional view of the brake pad according to 11 in the non-braking condition;

13 a detailed view XII of the brake pad according to 12 in the non-braking condition;

14 the detailed view XII of the brake pad according to 13 in braking condition.

In 1 is a schematic view of a disc brake 1 with a brake pad according to the invention 9 according to a first embodiment shown in the non-braking state. The disc brake 1 includes a caliper 2 , which is a brake disc 3 partially encloses, a Zuspanneinrichtung 4 as well as on both sides of the brake disc 3 arranged brake pads 8th . 9 , The caliper 2 is designed as a sliding or floating caliper or as a fixed caliper with axially displaceable disc. The application device 4 is a cylinder 5 upstream, which via a otherwise not shown here in detail Zuspannmechanik a pressure piston 6 acted upon initiation of a braking operation with a compressive force. Furthermore, in the application device is a compression spring 7 integrated, which a limited resilience of the pressure piston 6 serves. With the reference number 8th is the brake lining referred to, the piston side or zuspannseitig is arranged and the means of the pressure piston 6 against the brake disc 3 is pressed. With the reference number 9 is referred to the brake pad, the saddle back side or reaction side is arranged. The reaction side arranged brake pad 9 is due to the reaction force, which is due to the displacement of the formed as a sliding or floating caliper caliper 2 or at a fixed caliper by moving the brake disc 3 results, to the brake disc 3 pressed. The reaction-side brake pad 9 is a return spring 10 associated which on the caliper 2 is fixed. The reaction-side brake pad 9 also has an adjustment 11 on, which in the illustrated embodiment as a pair between the caliper 2 and the reaction-side brake pad 9 arranged sliding surfaces 12 . 13 is executed. The respective oppositely arranged sliding surfaces 12 . 13 are wedge-shaped.

Hereinafter, the course of a braking operation based on 1 to 6 portrayed. The force required for braking is achieved by pressing the application-side and reaction-side brake pads 8th . 9 by means of the application device 4 to the brake disc 3 generated. For this purpose, the application-side brake pad 8th and the reaction-side brake pad 9 be moved in the axial direction. This shift process can be divided into two phases. In the first phase of the application-side brake pad 8th and the reaction-side brake pad 9 shifted with little force within the so-called clearance and finally with the brake disc 3 brought into contact. In the second phase, the build-up of the contact force between the brake pads takes place 8th . 9 and the brake disc 3 ,

When initiating a braking operation, the application-side brake pad is first 8th to the brake disc 3 pressed, like in the 1 and 2 shown. Once the application-side brake pad 8th with the brake disc 3 comes in contact, is the slidably mounted caliper 2 as long shifted with a small force, to even the reaction-side brake pad 9 with the brake disc 3 comes into contact, as in 3 shown. Alternatively, a slidably mounted brake disc can be provided. As a rule, the disc brake 1 is actuated to a deceleration of the vehicle, there is the brake disc 3 in a rotary motion.

If now the reaction-side brake pad 9 with the rotating brake disc 3 comes into contact, occurs at the friction surface of the brake pad 9 a frictional force acting in the tangential direction. The reaction-side brake pad 9 is due to this frictional force acting on the friction lining side of the brake pad 9 attacks, taken around a small, geometrically limited amount in the tangential direction, since it is correspondingly tangentially movable here.

The between the caliper 2 and the reaction-side brake pad 9 arranged wedge-shaped sliding surfaces 12 . 13 cause due to the relative movement and a slight shift of the reaction-side brake pad 9 in the direction of the brake disc 3 , as 4 shows. The axial distance between the caliper 2 and the reaction-side brake pad 9 changes. The axial displacement of the reaction-side brake pad 9 by the sliding movement between the two ramped sliding surfaces 11 . 12 leads to a deflection of the return spring 10 , Thus, this axial displacement of the reaction-side brake pad 9 in the direction of the brake disc 3 is possible, it is necessary that the application device 4 , against the operating force of the pressure piston 6 by a small amount, a few tenths of a millimeter, can be pushed back. In the case of a pneumatically actuated disc brake, this is generally possible because the pressure medium (air) is compressible. In the case of a hydraulically actuated disc brake, this can be achieved by installing a compression spring or another compressible element with a correspondingly matched force / travel behavior. In the tangential direction of the adjustment of the reaction-side brake pad 9 due to the relative movement through one in the caliper 2 limited support contour.

The further course of the braking process now takes place in a known manner. To achieve the required delay, the contact pressure between the respective brake pad 8th . 9 and the brake disc 3 elevated. Here are the brake pads 8th . 9 according to their elasticities in the direction of the brake disc 3 postponed. Since the reaction-side brake pad 9 his working position has already reached during the application process, there is no difference in the performance of the disc brake 1 during braking compared to a conventional brake pad. When releasing the disc brake 1 become the brake pads 8th . 9 initially by the stored elasticity force in this from the brake disc 3 pushed back. Then the pressure piston 6 together with the application-side brake pad 8th through the in the application device 4 integrated (not shown) return spring actively returned. Due to this process, the brake pads 8th . 9 acting application force practically reduced to zero and as a result also the frictional force or tangential force on the brake pads 8th . 9 ,

By eliminating the tangential force can now be the reaction-side brake pad 9 by means of the return spring 10 that the caliper 2 and the reaction-side brake pad 9 connect with each other, be brought into the rest position. This is the friction lining side of the brake pad 9 in the tangential direction due to in the return spring 10 stored restoring force withdrawn. This slides the reaction-side brake pad 9 along the wedge-shaped sliding surfaces 11 . 12 in the tangential direction back, whereby the friction lining side of the brake pad 9 by a small amount, for example about 0.3 mm, from the brake disc 3 is pulled away, as from the 5 and 6 is apparent.

This ensures that the brake pads 8th . 9 in the unactuated state of the disc brake 1 no contact with the brake disc 3 exhibit. Thus, unwanted residual grinding torques can be avoided.

In 7 is a perspective view of a brake pad 9 shown according to a second embodiment. The reaction-side brake pad 9 includes a lining carrier 14 as well as a friction lining 15 , The friction lining 15 , which is a covering material 15a and a base plate 15b has, the latter preferably made of metal, the actual lining carrier 14 turned and the arrangement and stabilization of the actual covering material 15a serves.

Between the lining carrier 14 and the friction lining 15 are adjustment means 11 arranged. The lining carrier 14 and the friction lining 15 are by end to this arranged clamp-like spring elements 20 connected with each other.

The representation in 8th shows a longitudinal sectional view of the reaction-side brake pad 9 according to 7 in the non-braking state or idle state. In 9 is a detailed view VIII of the reaction-side brake pad 9 according to 8th shown in the non-braking state. The adjusting means 11 are as rolling elements 16 educated. The rolling elements 16 can, as in 9 shown, be cylindrical or have a spherical cross-section. The rolling elements 16 are by means of a flat guide element 17 preferably arranged equidistantly spaced from each other. For this purpose, the flat guide element 17 with the outer contour of the rolling elements 16 corresponding openings in which the rolling elements 16 are arranged on both sides in sections outwardly ersteckend. On the the guide element 17 each facing sides of the lining carrier 14 and the friction lining 15 respectively the base plate 15b are recesses 18 . 19 arranged, which with the outer contour of the planar guide element 17 projecting sections of the rolling elements 16 correspond. In the illustrated embodiment, the recesses 18 . 19 formed spherical or circular segment. Furthermore, the respective recesses 18 . 19 ramps on one side 21 . 22 on. The arrangement of the respective ramps 21 . 22 on the lining carrier 14 and on the friction lining 15 is opposite, that is, diagonally opposite each other.

In 10 is the detailed view VIII of the reaction-side brake pad 9 according to 9 shown in the braking state. As already stated above, when applying a braking operation, the application-side brake pad first becomes 8th to the brake disc 3 pressed. Once the application-side brake pad 8th with the brake disc 3 comes in contact, is the slidably mounted caliper 2 , or alternatively, the slidably mounted brake disc, as long as shifted with a small force, to even the reaction-side brake pad 9 with the brake disc 3 comes into contact. As a rule, the disc brake 1 is actuated to a deceleration of the vehicle, there is the brake disc 3 in a rotary motion. The contact of the reaction-side brake pad 9 with the rotating brake disc 3 leads to the occurrence of a friction surface of the brake pad 9 acting in the tangential direction frictional force. The reaction-side brake pad 9 is due to this frictional force acting on the friction lining side of the brake pad 9 attacks, taken around a small, geometrically limited amount in the tangential direction. Between the lining carrier 14 and the friction lining 15 occurs a relative movement. The between the lining carrier 14 and the friction lining 15 respectively the base plate 15b arranged as rolling elements 16 executed adjustment 11 cause due to the relative movement a small axial displacement of the friction lining 15 of the brake pad 9 in the direction of the brake disc 3 , Here, the rolling elements move 16 in the longitudinal direction or tangential direction of the brake pad 9 along the ramps 21 . 22 upwards, which is illustrated by the arrow BR. This relative movement leads to a change in the axial distance between the lining carrier 14 and the friction lining 15 the reaction-side brake pad 9 , The course respectively the slope of the ramps 21 . 22 determine the axial displacement of the brake pad 9 or the friction lining 15 with respect to the caliper 2 , In addition, the frictional force acting in the tangential direction causes the clip-like spring elements arranged at the end 20 changed in their position.

With the elimination of the by the application device 4 applied contact pressure and the active return of the pressure piston 6 eliminates the frictional force or tangential force on the brake pads 8th . 9 , The in the rolling elements 16 stored potential energy is now converted into kinetic energy, so that the rolling elements 16 into their starting position at the foot of the respective ramp 21 . 22 the recesses 18 . 19 return, which is illustrated by the arrow RB. Accordingly, the axial distance between the lining carrier changes 14 and the friction lining 15 , These take their starting position again in the non-braking state of the disc brake 1 one. This raises between the reaction-side brake pad 9 and the brake disc 3 the required spacing in order to avoid a residual grinding torque.

In 11 is a perspective view of a reaction-side brake pad 9 shown according to a third embodiment. This third embodiment differs in terms of adjustment 11 in that between the lining carrier 14 and the friction lining 15 transverse to the longitudinal axis of the brake pad 9 extending, pivotable about a tilt axis elements 24 are arranged, which are hereinafter referred to as tilting elements, as shown in the illustrations according to the 12 to 14 is apparent. The tilting elements 24 are arranged parallel to each other and extend in sections across the width of the brake pad 9 , The tilting elements 24 have a substantially slot-shaped cross-section. The circular arc-shaped ends of the tilting elements 24 stand with corresponding recesses 25 on the friction lining 15 engaged. On the lining carrier 14 facing side is at least one resilient return element 23 arranged. The reset element 23 has a substantially wavy contour. In the forming troughs is in each case a tilting element 24 arranged. To guide the tilting elements 24 or the resilient return element 23 are in the lining carrier 14 also recesses 26 intended. The contours of the respective recesses 25 . 26 correspond to the contour of the tilting elements 24 or the contour of the resilient return element 23 , The recesses 25 . 26 in the lining carrier 14 and in the friction lining 15 are arranged opposite each other, so that in the released position of the disc brake 1 the tilting elements 24 to the surface of the lining carrier 14 or the friction lining 15 are aligned inclined.

In 13 is a detail view XII of the brake pad 9 according to 12 in the non-braking state and in 14 the detailed view XII of the brake pad 9 according to 13 shown in the braking state. In the non-braking state, the tilting elements 24 inclined with respect to their longitudinal axis in a common direction, so that they are on a wall of the return element 23 issue. As already described above, the entrainment of the friction lining 15 due to the stiction due to contact with the brake disc 3 to a relative movement in the tangential direction of the reaction-side brake pad 9 , which is illustrated by the arrow BR. This relative movement between the lining carrier 14 and the friction lining 15 causes the tilting elements 24 be transferred to a substantially vertical position, wherein the distance between the lining carrier 14 and the friction lining 15 increased. The reset element 23 stores as a result of this tilting movement of the tilting elements 24 Deformation energy, which when releasing the disc brake 1 This causes the tilting elements 24 and with these the friction lining 15 , are returned to their initial position in the non-braking state, as illustrated by the arrow RB. This is done accordingly with a reduction in the distance between the lining carrier 14 and the friction lining 15 associated. This reduction ensures that there is between the reaction-side brake pad 9 and the brake disc 3 in the non-braking state an exemption of the reaction-side brake pad 9 adjusting, whereby a contact between the reaction-side brake pad 9 and the brake disc 3 is avoided.

LIST OF REFERENCE NUMBERS

1

 disc brake

2

 caliper

3

 brake disc

4

 application device

5

 cylinder

6

 pressure piston

7

 compression spring

8th

 Piston-side brake pad

9

 Reaction side brake pad

10

 Return spring

11

 adjustment

12

 sliding surface

13

 sliding surface

14

 lining support

15

 friction lining

15a

 covering material

15b

 baseplate

16

 rolling elements

17

 Flat guide element

18

 recess

19

 recess

20

 Clip-like spring element

21

 ramp

22

 ramp

23

 Tipping elements

24

 Return element

25

 recess

26

 recess

BR

 arrow

RB

 arrow

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102012006135 A1 [0007]

Claims (25)

Brake pad ( 9 ) for a disc brake ( 1 ) of a vehicle comprising a lining carrier ( 14 ) and a friction lining ( 15 ), which together have an axial thickness D, characterized in that between the lining carrier ( 14 ) and the friction lining ( 15 ) at least one adjusting means ( 11 ) is arranged, by means of which the friction lining ( 15 ) opposite the lining carrier ( 14 ) is relatively movable, wherein the relative movement of the lining carrier ( 14 ) to a change in distance between this and the friction lining ( 15 ) and leads to a change in the thickness D. Brake pad ( 9 ) for a disc brake ( 1 ) for a vehicle that has a caliper ( 2 ), wherein the brake pad a lining carrier ( 14 ) and a friction lining ( 15 ), characterized in that the brake pad ( 9 ) at least one adjusting means ( 11 ) is assigned, by means of which an axial distance between the caliper ( 2 ) and the friction lining ( 15 ) of the brake pad ( 9 ) is changeable. Brake pad ( 9 ) according to claim 1, characterized in that the friction lining ( 15 ) opposite the lining carrier ( 14 ) is relatively movable in the tangential direction. Brake pad ( 9 ) according to claim 2, characterized in that the brake pad ( 9 ) against the caliper ( 2 ) is relatively movable in the tangential direction. Brake pad ( 9 ) according to one of claims 1 to 4, characterized in that the at least one adjusting means ( 11 ) is adapted to produce a linear relative movement. Brake pad ( 9 ) according to one of claims 1 to 5, characterized in that the relative movement follows a ramp-shaped course. Brake pad ( 9 ) according to claim 6, characterized in that the at least one adjusting means ( 11 ) has a ramp-shaped contour. Brake pad ( 9 ) according to one of claims 6 or 7, characterized in that the at least one adjusting means ( 11 ) as two oppositely arranged wedge-shaped sliding surfaces ( 12 . 13 ) is executed. Brake pad ( 9 ) according to claim 8, characterized in that at least one sliding surface ( 12 . 13 ) on the caliper ( 2 ) and on the brake pad ( 9 ) is arranged. Brake pad ( 9 ) according to one of the preceding claims, characterized in that in the lining carrier ( 14 ) and the friction lining ( 15 ) mutually opposite recesses ( 18 . 19 ) are arranged, the inclusion of as adjusting means ( 11 ) trained rolling elements ( 16 ) serve. Brake pad ( 9 ) according to claim 10, characterized in that the rolling bodies ( 16 ) of a substantially flat between the lining carrier ( 14 ) and the friction lining ( 15 ) extending guide element ( 17 ) are included in sections. Brake pad ( 9 ) according to one of the preceding claims 10 or 11, characterized in that the recesses ( 18 . 19 ) one to the rolling elements ( 16 ) have adapted contour. Brake pad ( 9 ) according to claim 12, characterized in that the recesses ( 18 . 19 ) have a border area with a constant or variable pitch. Brake pad ( 9 ) according to one of the preceding claims, characterized in that the at least one adjusting means ( 11 ) is adapted to generate a nonlinear relative movement. Brake pad ( 9 ) according to claim 14, characterized in that the at least one adjusting means ( 11 ) as at least one element pivotable about a tilting axis ( 23 ) is executed, which with its ends in on the lining carrier ( 14 ) and the friction lining ( 15 ) arranged corresponding recesses ( 25 . 26 ) intervenes. Brake pad ( 9 ) according to claim 15, characterized in that the pivotable element ( 23 ) a resilient return element ( 24 ) assigned. Brake pad ( 9 ) according to one of the preceding claims, characterized in that the friction lining ( 15 ) a covering material ( 15a ) and a base plate ( 15b ) and that between the lining carrier ( 14 ) and the base plate ( 15b ) the at least one adjusting means ( 11 ) is arranged and / or formed. Brake pad ( 9 ) according to one of the preceding claims, characterized in that the lining carrier ( 14 ) and the friction lining ( 15 ) at their free ends by clip-like spring elements ( 20 ) are interconnected. Disc brake ( 1 ) for a vehicle having - a brake disc ( 3 ) comprehensive sliding caliper ( 2 ), - at least one application device ( 4 ) for applying the disc brake ( 1 ), which has a pressure piston ( 6 ), - at least one application-side brake pad ( 8th ) and a reaction-side brake pad ( 9 ), each comprising a lining carrier ( 14 ) and at least one friction lining ( 15 ), which on both sides of the brake disc ( 3 ) are arranged, - of which at least the application-side brake pad ( 8th ) by means of the application device ( 4 ) against the brake disc ( 3 ) is movable and the reaction-side brake pad ( 9 ) by means of the displaceable caliper ( 2 ) or the axially displaceable brake disc ( 4 ), characterized in that - at least the reaction-side brake pad ( 9 ) is designed according to one of claims 1 to 18. Disc brake according to claim 19, characterized in that the brake caliper and the reaction-side brake pad ( 9 ) at least one adjusting means ( 11 ) is assigned, by means of which an axial relative position between the caliper ( 2 ) and the friction lining ( 15 ) of the reaction-side brake pad ( 9 ) is changeable. Disc brake according to claim 19 or 20, characterized in that the at least one adjusting means ( 11 ) two oppositely arranged wedge-shaped sliding surfaces ( 12 . 13 ) having. Disc brake according to claim 21, characterized in that at least one sliding surface ( 12 . 13 ) on the caliper ( 2 ) as well as on the lining carrier ( 14 ) of the reaction-side brake pad ( 9 ) is trained. Disc brake according to claim 20, 21 or 22, characterized in that the reaction-side brake pad ( 9 ) and the caliper are tangentially and axially limited relative to each other displaceable. Disc brake according to one of claims 19 to 23, characterized in that the reaction-side brake pad ( 9 ) a fixed to him return spring ( 10 ), which in addition to the caliper ( 2 ) is fixed. Disc brake according to one of claims 19 to 24, characterized in that in the application device ( 4 ) a compression spring ( 7 ) is integrated, by which the pressure piston ( 6 ) against an actuating force of the application device ( 4 ) is rückverstellbar.

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