阅读说明：本技术 盘式制动器、盘式制动器的制动钳以及用于固定盘式制动器的制动衬片的压紧件和板簧 (Disk brake, brake caliper of a disk brake, and pressure piece and leaf spring for fixing a brake lining of a disk brake ) 是由 G·戈伊克 于 2018-04-17 设计创作，主要内容包括：本发明涉及一种盘式制动器,具有：制动钳(1),所述制动钳搭接能转动地设置在轴线(A)上的制动盘和在制动盘的两侧设置在衬片槽道(6)中的制动衬片(2、3)；沿横向在制动衬片(2、3)上分布的压紧组件(8),所述压紧组件包括刚性的压紧件(7)和板簧(9),所述压紧件(7)具有一个构成其总长度的大部分、在衬片槽道(6)上分布的中间部段(7b)和两个末端部段(7a、7c),所述压紧件朝盘式制动器轴线(A)支撑在制动衬片(2、3)上并以其第一末端部段(7a)延伸到制动钳(1)的缝隙(14)中,并且所述板簧(9)沿压紧件(7)的纵向延伸并且弹簧弹性地支撑在压紧件(7)的背向制动衬片(2、3)的外侧上。为了在装配和制造技术上将压紧组件的各元件的固定设计得较为简单,并且同时不会弱化固定,延伸到所述缝隙(14)中的第一末端部段(7a)相对于压紧件(7)的中间部段(7b)是弯折的。(The invention relates to a disk brake, comprising: a brake caliper (1) which engages a brake disk arranged rotatably on an axis (A) and brake linings (2, 3) arranged on both sides of the brake disk in lining channels (6); a pressure unit (8) which is distributed over the brake linings (2, 3) in the transverse direction and comprises a rigid pressure element (7) and a leaf spring (9), wherein the pressure element (7) has an intermediate section (7b) which forms a majority of the total length thereof and which is distributed over the lining channel (6) and two end sections (7a, 7c), wherein the pressure element is supported on the brake linings (2, 3) in the direction of the disc brake axis (A) and extends with its first end section (7a) into a slot (14) of the brake caliper (1), and wherein the leaf spring (9) extends in the longitudinal direction of the pressure element (7) and is spring-elastically supported on the outer side of the pressure element (7) facing away from the brake linings (2, 3). In order to simplify the fastening of the components of the pressure member assembly in terms of assembly and manufacturing technology, and at the same time not to weaken the fastening, the first end section (7a) extending into the gap (14) is bent in relation to the middle section (7b) of the pressure member (7).)

1. A disc brake includes: a brake caliper (1) which engages a brake disk arranged rotatably on an axis (A) and brake linings (2, 3) arranged on both sides of the brake disk in lining channels (6); a pressing assembly (8) distributed on the brake linings (2, 3) along the transverse direction, wherein the pressing assembly comprises a rigid pressing piece (7) and a plate spring (9), the pressing element (7) has an intermediate section (7b) which forms a majority of the total length thereof and which extends over the lining channel (6), and two end sections (7a, 7c), the pressure piece is supported on the brake linings (2, 3) in the direction of the disc brake axis (A) and extends with its first end section (7a) into a gap (14) of the brake caliper (1), and the leaf spring (9) extends in the longitudinal direction of the pressure piece (7) and is spring-mounted on the outer side of the pressure piece (7) facing away from the brake linings (2, 3), characterized in that the first end section (7a) extending into the gap (14) is bent relative to the middle section (7b) of the pressure piece (7).

2. The disc brake of claim 1, characterized in that the first end section (7a) is bent at an angle of 10 ° to 35 °, preferably 15 ° to 25 °, with respect to the middle section (7 b).

3. The disc brake of claim 1 or 2, characterized in that in the first end section (7a) there is a recess (7g) in which the leaf spring (9) engages with one of its ends.

4. The disc brake of one of claims 1 to 3, characterized in that the gap (14) is defined at least by a rear wall (14a), an upper inner surface (14b) facing the axis (A) and a lower inner surface (14c) facing away from the axis (A), and in that the upper inner surface (14b) is disposed obliquely at an angle (W) with respect to the axis (A).

5. The disc brake of claim 4, characterized in that the upper inner surface (14b) of the slot (14) has the same slope with respect to the middle section (7b) as the first end section (7 a).

6. The disc brake of claim 4 or 5, characterized in that the lower inner surface (14c) is also arranged obliquely at an angle to the axis (A), the lower inner surface (14c) preferably being arranged parallel to the upper inner surface (14 b).

7. The disc brake of one of claims 4 to 6, characterized in that the gap (14) is open in each case laterally to the pressure piece (7) in such a way that the gap (14) is delimited only by the rear wall (14a), the upper inner surface (14b) and the lower inner surface (14 c).

8. The disc brake of claim 3 in combination with claim 7, characterized in that the recess (7a) is open in the direction of the rear wall (14a) of the gap (14) and the upper (14b) and lower (14c) inner surfaces and is laterally bounded on both sides by side sections (7k) of the hold-down element (7).

9. The disc brake of one of the preceding claims, characterized in that the leaf spring (9) is spring-elastically supported on the upper inner surface (14b) of the gap (14) and externally on the intermediate section (7b) of the pressure piece (7).

10. The disc brake of one of the preceding claims, characterized in that the pressure-exerting element (7) is configured, at least in its middle section (7b), as a groove comprising an elongate base edge (7d) and side edges (7e, 7f) arranged on the sides of the base edge (7 d).

11. Brake caliper of a vehicle disc brake, comprising: a lining channel (6) for receiving a brake lining of a disc brake and a brake disc rotating on an axis (A); and a slot (14) for fixing one end of a hold-down assembly distributed over the lining channel (6) on the outside of the caliper, said slot (14) being defined at least by a rear wall (14a), an upper inner surface (14b) facing towards the axis (a) and a lower inner surface (14c) facing away from the axis (a), characterized in that the upper inner surface (14b) is arranged obliquely at an angle (W) with respect to the axis (a).

12. Brake calliper according to claim 11, wherein the angle (W) of the upper inner surface (14b) with respect to the axis (a) is 10 ° to 35 °, preferably 15 ° to 25 °.

13. Brake calliper according to claim 11 or 12, wherein the calliper has a material thickness (M) between the upper inner surface (14b) and the outer side of the calliper which increases starting from the pad channel (6), preferably in the form of a gradually widening wedge.

14. Brake calliper according to one of claims 11-13, wherein the lower inner surface (14c) is also arranged obliquely at an angle relative to the axis (a), the lower inner surface (14c) preferably being arranged parallel to the upper inner surface (14 b).

15. Brake calliper according to one of claims 11-14, wherein the rear wall (14a) of the slot (14) extends over an arc (27) with its centre outside the calliper and preferably above the lining channel (6).

16. Brake calliper according to one of claims 11-14, wherein the rear wall (14a) of the slot (14) consists of a straight middle section and a circular arc section adjoining the middle section without a step, the centre of the circular arc section being located outside the calliper and preferably above the lining channel (6).

17. Pressure-exerting element (7) for fixing a brake lining in a disc brake, having a longitudinal extent and a width which is small in relation to the longitudinal extent, the pressure-exerting element (7) having an intermediate section (7b) which forms a substantial part of its total length and which extends over a lining channel (6) of the disc brake, and two end sections (7a, 7c), characterized in that the first end section (7a) is bent in relation to the intermediate section (7 b).

18. An impaction element according to claim 17, wherein the first end section (7a) is bent at an angle of 10 ° to 35 °, preferably 15 ° to 25 °, to the intermediate section (7 b).

19. Pressing element according to claim 17 or 18, characterized in that the first end section (7a) has a recess (7g) for a leaf spring to fit in.

20. A pressing element as claimed in claim 19, characterized in that said recess (7g) has a U-shaped profile and is laterally delimited at two lateral sections (7k) by the pressing element (7).

21. Press element according to claim 19 or 20, characterized in that the recess (7g) is open upwards and downwards and at the end side facing away from the press element (7).

22. Pressure-exerting element according to one of claims 17 to 21, characterized in that it is configured, at least in its middle section (7b), as a groove comprising an elongate bottom edge (7d) and side edges (7e, 7f) arranged on the sides of the bottom edge (7 d).

23. A compression element as claimed in claim 22, characterized in that said side edges (7e, 7f) are provided along the bottom edge (7d) and the first end section (7a), respectively.

24. Press element according to one of claims 17 to 23, characterized in that the termination of the first end section (7a) forms an end side (7m) extending over an arc (27) with its centre outside the press element and preferably above the intermediate section (7 b).

25. Leaf spring (9) for a brake pad hold-down assembly of a vehicle disc brake, having two main sides (9.1, 9.2) and having a first spring end (9a), a spring intermediate section (9b) and a second spring end (9c) in succession, characterized in that the terminating portions of the respective spring ends (9a, 9c) each form a form-locking element (10a, 10c) which extends away from the main sides in opposite directions with respect to the main sides (9.1, 9.2), the first form-locking element (10a) being located on the first main side (9.1) and the second form-locking element (10c) being located on the second main side (9.2), and the leaf spring having at least two bends (9f, 9e) with opposite bending directions on the spring intermediate section (9b), wherein the bend (9f) located close to the first spring end (9a) is located on the second main side (9.2) on the outside, while the outer side of the curvature of the at least one further curvature (9e) is located on the first main side (9.1).

26. The leaf spring according to claim 25, characterized in that the bend (9f) provided close to the first spring end (9a) is provided on the first sixth of the total length of the leaf spring (9).

27. The leaf spring according to claim 25 or 26, wherein the bend (9f) arranged close to the first spring end (9a) is arranged at a distance of 1.5cm to 3cm from the first form-locking element (10 a).

28. The leaf spring according to one of claims 25 to 27, characterized in that the further curved portion (9e) is provided over the middle third of the total length of the leaf spring (9).

29. The leaf spring according to one of claims 25 to 28, characterized in that the width of the respective main side (9.1, 9.2) remains the same over the total length of the leaf spring (9).

Technical Field

The invention relates firstly to a disc brake having: a brake caliper that engages a brake disc rotatably disposed on an axis and brake pads disposed in pad channels on both sides of the brake disc; the clamping arrangement comprises a rigid clamping part and a leaf spring, wherein the clamping part has a middle section and two end sections which form the majority of the total length and are distributed on the lining channel, the clamping part is supported on the brake lining towards the disc brake shaft and extends into the gap of the brake caliper with the first end section, and the leaf spring extends along the longitudinal direction of the clamping part and is elastically supported on the outer side of the clamping part facing away from the brake lining.

The invention further relates to a brake caliper of a vehicle disc brake, comprising: a pad channel for receiving a brake pad of a disc brake and a disc rotatable on an axis; and a slot for fastening one end of the hold-down assembly on the outer side of the brake caliper distributed over the lining channel, said slot being delimited at least by the rear wall, an upper inner surface facing the shaft and a lower inner surface facing away from the shaft.

The invention also relates to a holding-down element for fastening a brake lining in a disc brake, which holding-down element has a longitudinal extent and a width that is smaller than the longitudinal extent, and which has an intermediate section that extends over the lining channel and two end sections that form a large part of its total length.

The invention finally relates to a leaf spring for a pressing arrangement of a brake lining of a vehicle disc brake, which leaf spring has two main sides and has a first spring end, a spring intermediate section and a second spring end in succession.

Background

Such a disc brake, such a brake caliper, such a pressure element and such a leaf spring part are known as a whole, partly as a single piece, from EP 1898115B 1. In order to fix and hold a brake lining arranged in a lining channel of a brake caliper of a disc brake, a two-part hold-down assembly extends over the lining channel and at the same time transversely over the brake lining arranged in the lining channel. The rigid pressure piece of the pressure unit is supported on the brake lining toward the disk brake shaft. This support is effected under spring force, for which purpose a leaf spring, which is fixed with one end relative to the brake caliper, extends externally along the pressure piece. The leaf spring applies a contact pressure to the contact pressure element in the direction of the disc brake axis, as a result of which the brake lining is held in its respective receptacle in the brake caliper or in the brake carrier. The pressure piece has such a length that it projects with one end into a recess in the brake caliper. The circumferential contour of the recess is adapted to the cross-sectional contour of the pressure piece, so that the pressure piece is fixed both radially with respect to the disc brake shaft and transversely to the disc brake shaft, both in the circumferential direction of the brake disc. However, such recesses cannot be produced simply because they are adapted to a large extent to the cross-sectional contour of the pressure piece, but instead a special milling cutter is required for producing said contour.

Disclosure of Invention

The object of the invention is therefore to make the fastening of the elements of the hold-down assembly simple in terms of assembly and production technology and at the same time not weaken the fastening.

For this purpose, in the disk brake having the features described above, it is proposed that the first end section of the pressure piece, which extends into the gap of the brake caliper, is bent relative to the middle section of the pressure piece.

This has the advantage in terms of assembly technology that the pressure piece can be moved into the gap of the brake caliper, preferably with an obliquely extending movement. This results in a solution which is particularly space-saving and nevertheless enables a stable fastening of the pressure piece. In particular, the space-saving solution is advantageous for a vehicle disc brake because the outside of the caliper has only a small radial distance from the wheel or vehicle rim rotating around the caliper. In particular, only a very limited space is available in the region of the lining channel for the stable fastening of the pressure element or of the structural unit comprising the pressure element and the leaf spring.

Since the slot in the brake caliper accommodating the end of the pressure piece and the leaf spring is arranged at an angle to the axis of rotation of the brake disk, this end of the pressure assembly can be fixed in a stable manner on the brake caliper with a reduced space requirement.

Particularly advantageous here is an embodiment in which the angle at which the gap is arranged relative to the axis of rotation is between 10 ° and 35 °, preferably between 15 ° and 25 °. In accordance with one embodiment of the pressure element, the first end section of the pressure element is bent at an angle of 10 ° to 35 °, preferably 15 ° to 25 °, relative to the middle section. In particular an angle of about 20 is advantageous. That is, it is advantageous if the slot has the same inclination relative to the middle section as the first end section of the pressure piece. This means that the first end section of the pressure piece and the slot are inclined at the same angle to the brake disk axis. This can be achieved simply in terms of manufacturing technology.

Preferably, the slots are each open in the lateral direction of the pressure element. That is, the gap is defined only by a rear wall, an upper inner surface facing the axis of rotation of the brake disc and a lower inner surface.

The simple laterally open shape of the slot allows the slot to be produced in a simple manner, for example directly by casting or by simple machining of the brake caliper by means of a milling cutter. Here, the upper inner surface, the lower inner surface and the side wall of the slit can be simply shaped and processed. The machining can be carried out by means of a disc cutter in a single machining movement by moving the disc cutter in an inclined movement into the brake caliper in the direction of the depth of the gap. The rear wall of the slit thus obtains a circular arc shape.

In addition, it is possible that after the maximum insertion of the disc cutter in the direction of the depth of the slot, the disc cutter is slightly moved laterally and then retracted. In this case, the rear wall of the slot consists of a straight middle section and a circular arc section connected without steps to the middle section, the center of the circular arc section being located outside the brake caliper and preferably above the lining channel.

It is furthermore advantageous according to the invention if the recess provided on the first end section of the pressure piece is open in the direction of the rear wall of the slot and in the direction of the upper and lower inner surfaces of the slot, and is laterally delimited on both sides by the side sections of the pressure piece.

The recess preferably has a U-shaped profile. In the mounted state, the end-side opening of the U-shaped recess faces the rear wall of the gap on the caliper side. The leaf spring engages with its one end in the recess and preferably with its entire width.

In this case, it is particularly advantageous if the leaf spring is supported elastically at least on the upper inner surface of the slot and externally on the middle section of the pressure element. This ensures that the holding-down element is fixed on one side in a direction perpendicular to the brake disk axis relative to the brake lining or brake lining and on the other side relative to the brake caliper. By means of this simple fastening, the production expenditure for the component is significantly reduced.

For the pressure piece and its stability, it is advantageous if the pressure piece is formed at least in its middle section as a groove made of an elongated base and lateral edges arranged on the sides of the base. The two side edges can also be additionally elongated in that they are arranged not only along the base edge but also along the first end section.

In the case of a brake caliper according to the invention, it is proposed that at least the upper inner surface of the slot formed in the brake caliper is arranged at an angle to the axis of rotation of the brake disk. This angle is preferably between 10 ° and 35 °, particularly preferably between 15 ° and 25 °.

In order to avoid weakening the brake caliper in the region of the fixed hold-down assembly, a particularly advantageous embodiment of the brake caliper provides that the material thickness of the brake caliper between the upper inner surface of the slot and the outer side of the brake caliper increases proceeding from the lining channel. Preferably the material thickness increases in the form of a widening wedge.

In order to make the slot possible with a standard disc cutter, it is preferred that the lower inner surface of the slot is also arranged at an angle to said axis, where said lower inner surface is preferably arranged parallel to the upper inner surface.

A configuration of the rear wall of the slot can be achieved by using a rotary disc cutter, i.e. the rear wall extends over a circular arc, the center of which is located outside the brake caliper and preferably above the lining channel. In addition, it is possible that after the maximum insertion of the disc cutter in the direction of the depth of the slot, the disc cutter is slightly moved laterally and then retracted. In this case, the rear wall of the slot consists of a straight middle section and a circular arc section connected without steps to the middle section, the center of the circular arc section being located outside the brake caliper and preferably above the lining channel.

In an embodiment of the invention, the first end section of the pressure piece is bent with respect to the middle section.

The first end section of the pressing member has a recess for fitting the leaf spring.

This, together with the other components of the disc brake, enables a simplified mounting of the holding-down element relative to the brake caliper and the brake pad or brake lining. This is particularly helpful when the first end section is bent at an angle of 10 ° to 35 °, preferably 15 ° to 25 °, relative to the middle section.

The recess preferably has a U-shaped contour in the region of the first end section of the pressure piece and is delimited laterally on both sides by side sections of the pressure piece. The side sections are of course not separate components. Instead, the recess is machined into the preformed pressing element, for example by punching or milling. The recess can also be shaped directly during the production of the pressure piece. The recess is open upward and downward and at the end face away from the pressure piece.

The pressure means is preferably formed at least in its middle section as a groove comprising an elongate base and side edges arranged on the sides of the base. The side edge mainly realizes the strengthening of the pressing piece.

The width of the groove is preferably equal to the width of the recess in the end section of the pressure piece.

In respect of the pressure element and its stability, it may be advantageous to additionally elongate the two side edges in such a way that they are arranged not only along the base edge but also along the first end section. The additional side section can be used to additionally laterally support a pressure piece which is mounted in a slot of the brake caliper.

Furthermore, it is advantageous if the terminating portion of the first end section forms an end face which extends on a circular arc, the center of which is located outside the pressure piece and preferably above the intermediate section.

In the case of the leaf spring according to the invention, it is proposed that the terminating portions of the spring ends each form a form-locking element which extends away from the main side in the opposite direction with respect to the main side, so that a first form-locking element is located on the first main side and a second form-locking element is located on the second main side. Furthermore, the leaf spring has at least two bends or kinks on the spring intermediate section, the bends or kinks having opposite bending directions. The outer side of the bend arranged close to the first spring end is located on the second main flank, while the outer side of the bend of the at least one further bend is located on the first main flank.

The first of the bends is intended to advantageously adapt the longitudinal profile of the leaf spring to the configuration of the slot and in particular to the inclination of the upper inner surface of the slot. The additional curved portion is instead designed to rest on the outer side of the pressure element and to apply a spring force to the pressure element in the direction of the brake lining.

According to one embodiment of the leaf spring, the first bend, i.e. the bend located close to the first spring end, is located on the first sixth of the total length of the leaf spring. Preferably, the first bend is arranged at a distance of 1.5cm to 3cm from the first form-locking element.

In contrast, the second bend, which is intended for external support on the pressure element in the installed state, is preferably arranged in the middle third of the overall length of the leaf spring.

According to a further embodiment of the leaf spring, the width of the main flanks remains the same over the entire length of the leaf spring.

Advantageous embodiments of the disk brake and of the pressure element are given in the respective dependent claims.

Drawings

Specific embodiments of the disk brake, the brake caliper, the pressure element and the leaf spring are explained in detail below with reference to the drawings. Wherein

FIG. 1 shows a perspective view of a brake caliper of a vehicle disc brake, including a lining channel formed in the brake caliper with a brake lining disposed therein, and a hold-down assembly above the lining channel;

fig. 2 shows an enlarged view of the contents according to fig. 1, but without showing the components of the hold-down assembly shown in its entirety in fig. 1;

FIG. 3 shows the contents according to FIG. 1 in a longitudinal section through a brake caliper;

fig. 3a shows a longitudinal section corresponding to fig. 3, but only of the brake caliper itself and additionally shows the disc cutter positioned in front of the brake caliper in the machining position;

FIG. 4 illustrates the area to the left of FIG. 3 on an enlarged scale;

FIG. 5a shows the area to the left of FIG. 1 on an enlarged scale;

FIG. 5b shows the same area as FIG. 5a, but without the brake pad;

FIG. 6 shows a perspective view of only the brake lining with the backing plate facing the viewer;

FIG. 7 shows a perspective view of a hold down used on a caliper showing only the hold down assembly;

FIG. 8 shows a perspective view of only the leaf spring used on the caliper as an integral part of the hold-down assembly;

fig. 9 shows a perspective view of only the leaf spring and the pressing member as main components of the pressing assembly;

fig. 10 shows a perspective view of only the bracket used on the brake caliper, which bracket serves simultaneously as a bearing element and as a locking element;

fig. 11 shows a perspective view of a second embodiment of the pressure piece; and

fig. 12 shows the pressure piece according to fig. 11 in a longitudinal section.

Detailed Description

Fig. 1 to 3a show a central part of a brake caliper 1 for a vehicle disc brake of a truck. Fig. 2 shows the brake caliper in an enlarged view. Fig. 3 and 3a show the brake caliper in a longitudinal sectional view. The disc brake may be of the sliding caliper type or of the fixed caliper type. One brake lining is arranged on each side of the brake disk, which is shown only by its axis of rotation a (fig. 3). For receiving the brake linings 2, 3, the brake caliper 1 is provided with lining channels 6, on which lining clips 7 extend. The lining clips 7 span the lining channel 6 in such a way that the lining clips 7 extend in the transverse direction over the two brake linings 2, 3, that is to say over the brake lining 2 arranged on the outside relative to the vehicle and the brake lining 3 arranged on the inside relative to the vehicle, which are designed differently here.

The brake linings 2, 3 are each formed from the actual friction lining 4 and the backing plate 5 according to fig. 4. The back plate 5 is preferably made of cast metal. The back plate 5 serves to distribute the brake pressure better over the lining surface. The back plate also has the function of guiding and supporting the brake lining on the caliper 1 itself or on a brake carrier fixed relative to the axis.

The lining holding-down element 7, which is shown in fig. 7 as a single piece, is elongated along a longitudinal center line L1 and extends with a large portion of its length parallel to the axis a of rotation of the brake disk. If the first end section 7a of the pressure piece 7 shown on the right, i.e. the end located inward with respect to the vehicle, is accommodated directly in the brake caliper 1, for this purpose the first end section 7a of the pressure piece 7 engages in a slot 14 (fig. 3) of the brake caliper 1. The other end 7c of the pressure piece 7 is fixed directly to the caliper 1, mainly by means of a pin, as will be explained in more detail.

In order to fix the two brake linings 2, 3 in the lining channel 6, the hold-down element 7 is designed as a rigid bracket and forms a hold-down assembly 8 (fig. 3) with a flexurally elastic leaf spring 9. The two-part pressure unit 8 has the task of fixing the two brake linings 2, 3 relative to the lining channel 6 in such a way that the brake linings 2, 3 cannot move or fall out of the lining channel 6 radially outward relative to the axis of rotation a of the brake disk.

The pressure-exerting element 7 has a channel-like cross section over a large part of its total length and in particular over its central section 7b, with a base 7d which is arranged on the longitudinal center line L1 of the pressure-exerting element 7 and to which side edges 7e, 7f are connected along the two longitudinal edges of the base 7d, which reinforce the central section 7b of the pressure-exerting element 7 against bending forces.

The flat bottom of the groove, which is formed by the bottom edge 7d, has approximately the width of the leaf spring 9, on which the side edges 7e, 7f are connected on both sides at an angle of between 15 ° and 90 °.

The pressure piece 7 bears with its bottom edge 7d directly against the upper edge of the lining back plate 6 of the brake lining 3 located inside. At the same time, the lateral edges 7e, 7f of the pressure piece are supported laterally and against the stop 5a on the upper edge of the lining carrier 5. The two stops 5a prevent the pressure piece 7 from being able to move significantly sideways relative to the brake lining 3 located inside.

The leaf spring 9, which is made of spring steel, likewise extends on the longitudinal center line L1. The leaf spring is fixed with one spring end 9a in a first spring support and with the other spring end 9c in a second spring support. Both fastening portions are releasable in order to remove the spring 9 and the lining clips 7 arranged underneath the spring and thus to be able to access the lining channel 6 from the outside for the exchange of the brake linings 2, 3.

The leaf spring 9 extends longitudinally with respect to the pressure piece on the outside of the pressure piece 7 and is supported from the outside on the pressure piece 7, in particular in the region of the base 7d on the middle section 7b of the pressure piece (fig. 3, 9), as a result of which the pressure piece is spring-loaded toward the two brake linings 2, 3. The pressure means 7 is therefore supported both on itself rigidly with continuously acting spring forces on the two brake linings 2, 3 and acts on the latter with a force directed in each case toward the axis of rotation a.

According to fig. 8 and 9, the leaf spring 9 is supported on the lining pressing means 7 on the outside only by a short longitudinal section designed as a bend or bend 9 e. Thus, on this short longitudinal section, which is located in the middle third of the length of the leaf spring 9 and above the lining channel 6, the leaf spring 9 is provided with a bend or bend 9e, which extends transversely to the longitudinal extension of the leaf spring 9. The middle section of the leaf spring is connected to both sides at the bend 93. However, the leaf spring 9 rests only on the middle section 7b of the pressure element 7 with the outer side of the bend 9 e. Only in this directly applied position is the spring force applied to the pressure means 7 in the direction of the brake lining.

According to fig. 8, the leaf spring is generally characterized by its upper main side 9.2, its lower main side 9.1 and also by a first spring end 9a, a spring intermediate section 9b and finally a second spring end 9c arranged one behind the other in the longitudinal direction. The leaf spring 9 has a constant width over its entire length, which simplifies the manufacture.

The outermost terminations of the spring ends 9a, 9c form a form-locking element 10a, 10c, respectively, which is a fold relative to the main extension direction of the leaf spring. The form-locking elements 10a, 10c extend in opposite directions away from the leaf spring-side main direction of extension with respect to the main sides 9.1, 9.2, so that the first form-locking element 10a is located on the first main side 9.1 and the second form-locking element 10c is located on the second main side 9.2.

The leaf spring 9 has two bends or bends 9f, 9e in opposite bending directions in its middle section 9b, wherein the bend 9f located close to the first spring end 9a has its outer side on the second main side 9.2 and the other bend 9e has its outer side on the first main side 9.1.

The bent-over portion 9f is located in the assembled state in particular outside the slot 14 in the brake caliper, that is to say in front of the slot opening. Only a short flat spring section 9d is then provided between the bend 9f and the spring end 9a with the form-locking element 10 a. The length of the spring section is less than one sixth of the total length of the leaf spring. The leaf spring 9 is supported mainly by this shorter spring section 9d on the upper inner surface 14b of the slot 14 in the brake caliper.

The other, oppositely curved portion 9e is arranged centrally and on the middle third of the leaf spring length in the middle section 9b of the leaf spring.

A first spring support for the leaf spring 9 is located on the brake caliper 1 in the form of a slot 14, inwardly with respect to the vehicle, and a second spring support is located beside the lining channel 6, outwardly with respect to the vehicle. The spring support, which is located outside the vehicle, has a pin 13 for fixing the associated spring end 9c of the leaf spring 9. In contrast, the brake caliper 1 is provided with a recess in the form of a slot 14 which opens into the lining channel 6 in order to form a spring support which is located inward with respect to the vehicle. This gap simultaneously provides a location for the end of the pressure element 7, which gap is also used for the leaf spring end 9a in the case of leaf springs, i.e. for the shorter end section of the leaf spring 9, which is less than 3cm long.

In order to mount the hold-down assembly 8, which comprises the hold-down element 7 and the leaf spring 9, it can be advantageous if the ends of the two components, which are jointly introduced into the gap of the brake caliper 1 with a movement extending obliquely, are locked to one another in the longitudinal direction. For this purpose, the pressure piece 7 is provided with a recess 7g at this end (fig. 7 and 11). The form-locking element 10a of the leaf spring 9, which is bent downward toward the brake caliper, engages in a form-locking manner in said recess, like a hook, in the loop associated therewith. This longitudinal locking of the leaf spring 9 on the pressure piece 7 is such that, once the end 7a of the pressure piece 7 is located in the slot 14 of the brake caliper 1, the leaf spring 9 is locked in the longitudinal direction, that is to say in the axial direction, on the pressure piece 7. The height of the slot 14 and the length of the form-locking element 10a extending transversely thereto are designed such that the form-locking element 10a cannot be disengaged from the recess 7g of the pressure piece 7 in the slot 14, as a result of which the locking is achieved.

This measure serves to achieve safety and makes it possible to subsequently easily fix the pressure element 7 and in particular the leaf spring 9 at its other end, that is to say in the region of the spring bearing shown to the left, which is located outside the vehicle.

The slot 14 formed in the brake caliper 1 is correspondingly open in the lateral direction of the pressure piece 7, so that said slot 14 is only delimited by the rear wall 14a, the upper inner surface 14b and the lower inner surface 14c of the brake caliper. The upper inner surface 14b here refers to the wall of the slot 14 facing the axis or rotation axis a of the disc brake. The lower inner surface 14c refers to the wall of the slot 14 facing away from the axis or axis of rotation a. The two inner surfaces 14b, 14c preferably extend parallel to one another, i.e. in this case define a parallel gap.

The pressure piece 7 is bent, i.e. inclined, at its end section 7a relative to the middle section 7 b. After the bending, the end section 7a of the holding-down part 7 extends completely straight to the end side 7m opposite the rear wall 14a, i.e. is not bent or bent. In the mounted state, the center line L1 of the pressure element 7 is oriented substantially parallel to the brake disk axis a. Only the end portion 7a is inclined or bent by 10 ° to 35 °, preferably 15 ° to 25 °, and particularly preferably 20 °, relative to the center line L1 and thus also relative to the brake disk axis a.

According to fig. 3a, the slot 14 in the brake caliper 1 is also arranged inclined to the axis a in the direction of its slot depth. The angle a of the oblique position relative to the axis a is substantially the bending angle of the oblique end section 7a of the pressure piece 7. The leaf spring 9 is thus supported under spring force on the upper inner surface 14b of the slit 14 facing the axis a.

Fig. 3a shows a method for producing the slot 14 by means of a milling cutter F. Thus, the slot can be made simply by the simple shape of the slot 14 lacking sidewalls.

By means of a disc mill F rotatable on the axis a, the upper inner surface 14b of the slot, the lower inner surface 14c parallel thereto and the rear wall 14a can be machined by a single feed corresponding to the double arrow shown in fig. 3 a. That is, the machining is carried out by a single forward movement and a subsequent return movement of the disc cutter F. This movement is at an angle W and perpendicular to the mill axis a 3.

The width of the disc cutter F determines the height of the gap 14 achieved. The feed direction of the disc cutter F is such that the formed rear wall 14a of the slot is not flat but has the shape of a circular arc, the center of which is located outside the slot 14. This circular arc 27 is shown in fig. 7 and 11, but here with reference to a corresponding circular contour of the end side 7m of the brake caliper 1. The imaginary centre of the circular arc 27 is located outside the caliper, that is to say externally above the lining channel 6.

Alternatively, it is possible that, when the disc cutter F is maximally moved in the depth direction of the slot 14, it is slightly moved laterally and then retracted. A rear wall 14a is formed, which consists of a straight middle section and a circular arc section connected without steps to the middle section, the center of the circular arc section also being located outside the caliper above the lining channel 6.

Since the upper inner surface 14b of the slit 14 is inclined at the angle W, an advantage is achieved in the strength of the caliper 1. Since the brake caliper 1 has a material thickness M (fig. 3) between the upper inner surface 14b and the outside of the brake caliper, the material thickness M increases significantly from the lining channel 6, i.e. in the form of a widened wedge. Furthermore, this important position of the brake caliper 1 saves valuable space. Since there is only a small radial distance to the vehicle or vehicle rim around which the caliper rotates at this location outside the caliper. In particular in the region around the lining channel, there are usually only limited positions for fastening the pressure element 7 or the structural unit consisting of the pressure element 7 and the leaf spring 9.

The recess 7g of the pressure piece 7 is open in the direction of the rear wall 14a, the upper inner surface 14b and the lower inner surface 14c of the slot 14, but is delimited in the lateral direction, that is to say in the direction of the lateral opening of the slot 14, by the lateral sections 7k of the first end section 7 of the pressure piece 7. The side sections 7k also extend obliquely to the intermediate section 7b, since they are integral parts of the first end section 7a which extends generally obliquely to the intermediate section 7 b. That is, the recess 7g also has a U-shaped profile or contour which opens upwardly and downwardly, wherein the end side opening of the U-shaped recess 7g points in the direction of the rear wall 14a of the slot 14.

According to fig. 7, the second end section 7c of the pressure element 7, which is located at the outside with respect to the vehicle, is designed with a narrower width B than the longer longitudinal or central section 7B, which has the shape of a groove. The width B is not greater than the width of the base 7d at the end section 7 c. The pressure-exerting means 7 is provided, mainly in this end section, with a meandering structure 11 connected to an elongate base 7d, in that the pressure-exerting means 7, starting from the base 7d, first has a first downward bend 11a and a second bend 11 connected thereto as a reverse bend. A straight longitudinal section 12 is directly connected to the second bend 11b as the end of the pressure piece 7 facing outward with respect to the vehicle. In this way, the straight longitudinal section 12 is lower or closer to the axis of rotation a than the bottom edge 7c of the groove-shaped middle section 7 b.

The S-shaped meander 11 is preferably designed such that its second bend 11b, which transitions directly into the straight end section 12, is not directly connected to the first bend 11a, but rather a short, straight section 11c is also provided between them. The angle thereof with respect to the longitudinal section of the channel-like shape is, for example, 110 °.

The longitudinal sections 12 extend over the length L substantially parallel to the axis of rotation a and are offset parallel to the substantially longer, groove-like central section 7 b. For example, the pressure piece 7 may have a total length of about 150 mm. The end section 12 then extends offset by 15 to 20mm with respect to the base 7d of the groove-shaped section.

The area of the meandering structure 11 can be reinforced by one or more stiffening depressions 11d, since the pressure piece 7 is here narrower by the width B and bending forces can occur. The pressure piece 7 is preferably made of stamped and deformed steel sheet with a material thickness of at least 4 mm.

As regards the pins 13 mounted on the caliper, they are overlapped from below without contact by the labyrinth 11 or from the longitudinal section 12 constituting the end of the second end section 7c of the pressure piece 7 (fig. 4). Nevertheless, this end region of the pressure piece 7 is blocked by the pin 13 arranged above in such a way that the clamping piece cannot be released from the lining channel 6 from the outside in any case. The end of the meandering structure 11 or the longitudinal section 12 as the second end section 7c of the pressure piece 7 has such a height distance in the mounted state to the pin 13 that no contact occurs.

The pressure piece 7 is supported from above on the back plate 5 of the two brake linings 2, 3 and can be moved in its longitudinal direction only, but is held fixed transversely thereto by the brake lining-side shaping elements. The two brake linings 2, 3 are freely movable in the lining channel 6 in the direction of the axis of rotation a of the brake disk and are guided with a defined play in the circumferential direction of the brake disk. The combination of these degrees of freedom of movement makes it possible for the pressure piece 7 to move freely on the brake lining 3 along its longitudinal extent and to be mounted in a laterally limited or floating manner with respect to the brake linings 2, 3. In the assembled state, this movement is tightly limited in its longitudinal extension by corresponding stops on the brake caliper 1. For this purpose, the stop surfaces between which the pressure piece 7 can move are machined, for example by milling the brake caliper 1.

The projections 15 molded onto the brake caliper 1 are arranged longitudinally opposite the second end section 7c of the holding-down element at a small distance. The projection 15 thus forms a stop which limits the longitudinal mobility of the pressure piece 7 to the outside of the vehicle. Preferably, the protrusion 15 extends all the way around the periphery of the pin 13, but does not contact the pin 13.

The two bearing blocks 50, which are integrally molded on the caliper 1, each have a hole, in which the pin 13 is mounted on the axis 13 a. In order to prevent the pin 13 from being able to be removed from the bearing block 50 and thus from the brake caliper 1 in the longitudinal direction of the pin, a suitable securing ring, cotter pin or the like is provided on the pin 13.

Fig. 1 and 3 show details of the fastening of the spring end 9c of the leaf spring 9 to the support, which is located on the outside of the vehicle. The spring support comprises, in addition to the pin 13, a fastening bracket 60, which is connected to the brake caliper 1 by the pin 13 so as to be able to pivot about a pin axis 13 a. The leaf spring 9 is supported with its spring end 9c on the inner side or lower side of the bracket 60 facing the axis 13 a. At this spring end 9c, the leaf spring is provided with an upwardly extending form-locking element 10 c. This form-locking element 10c engages in a slot-like opening 61 in the bracket 60 and thereby fixes the pivot position of the bracket 60.

The bracket, which is shown as a single piece in fig. 10, is an outer bearing element for the leaf spring 9 relative to the vehicle. The bracket 60 consists of an intermediate section 62 parallel to the axis 13a, on which the opening 61 can be located, and two lateral sections 63 arranged substantially at right angles to the intermediate section 62 (fig. 10). The side sections are designed as webs 63 and are each provided with a circular opening 66 arranged on the axis 13 a. Since the two openings 66 are flush with each other on the axis 13a, the axis 13a is simultaneously the alignment axis of the two openings 66. The pin 13 passes through both openings simultaneously.

The edge of the tab 63 facing the disc brake rotation axis a has an edge profile 64 which is curved towards the axis 13 a. The profile section of the profile 64 facing the disc brake axis a forms a stop, since the profile run is designed such that the profile 64 has a greater distance a1 from the axis 13a in part and a smaller distance a2 in part. For example, the profile 64 is eccentric or it may be circular but now offset with respect to the axis 13 a.

The pin 13 is a fastening mechanism for releasably fastening the bracket 60, which serves as a support element and a locking element, to the brake caliper 1. At the same time, the end 9c of the leaf spring 9 rests under spring tension on the inner side of the middle section 62 facing the pin 13. The inner side is thus a seat 62a on which the spring end 9c rests. The sum of these measures achieves a reliable fixing and resistance to bending stresses in the leaf spring 9.

An additional safeguard is that the upwardly bent form-locking element 10c formed on the outermost spring end 9a engages in the opening 61 of the workpiece 60.

The assembly of the lining hold-down element 7, the leaf spring 9, the pin 13 and the bracket 60 as a bearing element and locking element is mounted in such a way that the leaf spring 9 is initially placed with its end 9a on the hold-down element 7 in such a way that the leaf spring 9 engages in a positive-locking manner in the recess 7g of the end section 7a of the hold-down element 7 that is located in the interior of the vehicle. Thereafter, the temporarily attached components, i.e., the pressing member and the plate spring, are inserted into the slit 14 in a movement extending obliquely. The first end section 7a, which is bent relative to the middle section 7b, is then at least partially located, together with the leaf spring 9, inside the slot 14, which is inclined toward the brake disk axis a. The pressure piece 7 is then pivoted downward at its other end until it reaches the pressure piece surface 43. Here, the pressure means is simultaneously placed from above between the two stops 5a on the back plate 5 of the brake lining 3 in relation to the vehicle.

In a next step, the bracket 60 is placed onto the other spring end 9c, which can be made easier and thus safer for the installer by inserting the form-locking element into the opening 61 of the bracket 60. The end 9c of the spring 9 is supported on the inside on the support 62a on the bracket 60. The bow 60 is now moved downward by applying pressure only manually and bending the leaf spring until the pin 13 enters the bearing block 50 along the axis 13a and simultaneously passes through the opening of the bow 60. The application of pressure to the bracket 60 can then be ended, since the tension of the leaf spring 9, in combination with the pin 13, is reliably absorbed by the bracket 60, which constitutes the bearing element.

The leaf spring 9 holds the pressure element 7 with spring bias against the brake linings 2, 3 and ensures that the outwardly lifted brake linings are pressed back into their original position again in the event of a strong impact, for example when driving over a pothole. If the leaf spring 9 breaks, for example, due to mechanical influences and thus loses its retaining function, the brake lining is not lost by the bracket 60 arranged above it and the hold-down element 7 being held at all times by the slot 14.

The zigzag structure 11 of the second, narrower end section 7c of the pressure element 7 on the side of the brake disk facing outwards with respect to the vehicle, which is shown in fig. 7, has the advantage that in this region the disk brake part projects less far radially outwards in this region and thus contributes to relieving the tension in the installation space between the surrounding wheels rotating about the brake. However, the meander 11 also generates a certain position requirement in the region of the brake linings 2 arranged on the wheel outer side of the brake disk. It is therefore designed in a special way, as explained in detail below.

According to fig. 6, the brake lining 2 arranged on the outer side of the brake disk with respect to the vehicle is composed of a friction disk 4 for bearing against a stop disk and a stable back plate 5. The back plate is made of, for example, cast steel, wherein the front side is designed as a fastening surface 6 for the friction lining 4, and the rear side 17 is designed as a pressure surface for transmitting the brake pressure. As a result of this rear face 17, the back plate 5 rests against a corresponding pressure-exerting face 18 of the brake caliper 1. The face 18 is at the same time a wall of the lining channel 6.

The peripheral contour of the back plate 5 is defined by an upper or outer edge 21 with respect to the axis of rotation a, an inner or lower edge 22 facing the axis of rotation a, and two side edges 23a, 23b extending between the upper and lower edges, which extend parallel to one another.

The upper or outer edge 21 is characterized by a main tendency which takes the shape of a brake disc. For this purpose, the upper edge 21 has a profile which is essentially circular in shape, i.e. over a large part of its length, and which forms a circle on the circumference of the circular brake disk. This has the advantage that the brake lining 2 does not project radially outward beyond the technically necessary circumference of the brake disk.

The back plate 5 is supported in the circumferential direction by means of the two lateral edges 23a, 23b, so that the braking torque is transmitted to the brake caliper 1 or alternatively to a brake carrier of the disk brake, which carrier is mounted fixed relative to the axis. The transmission of the braking torque to the caliper support via the lower edge of the back plate 5 can also be effected on a smaller scale when a brake support is present.

The friction lining 4 on the upper or outer edge 31 is also characterized by a main tendency which takes the shape of a brake disc. For this purpose, the upper edge 31 has a circular arc-shaped profile, which is circular on the circumference of the circular brake disk, mainly, i.e. over a large part of its length, so that this edge does not project radially outward beyond the circumference of the brake disk, but at the same time provides the greatest contact surface between the friction lining 4 and the brake disk.

If the edges 21, 31 have a substantially arc-shaped trend, this trend includes individual deviations from this main design form. In this way, an elongated recess 33 for fastening an electric brake lining wear sensor can be provided eccentrically in the friction lining 4 and the back plate 5. Furthermore, it is possible to mold individual small projections on the edge 21 without affecting the modified curved body design, which projections may be advantageous, for example, in the production of brake linings.

In order to achieve a position and free space for the meandering structure 11 of the hold-down element 7, the main course of the upper edge 21 of the back plate 5 is interrupted by a local recess 25 of the edge 21, just at the midpoint between the two lateral edges 23a, 23b of the back plate 5. This depression is wider than the width of the bent-over pressure piece section.

Only in the region of the recess 25, the height of the back plate 6 is thus reduced radially with respect to the distance to the axis of rotation a, so that a free space is formed in the back plate 5, through which the pressure piece 7 extends with at least a part of its cross section.

Likewise, in order to provide a location for the pressure piece 7, the friction lining 7 also has free space in the same region. In this way, the friction lining 4 also extends on its outer edge 31 in a predominantly arcuate manner, the design of the main body also being interrupted at the midpoint between the two side edges 23a, 23b by the recess 35 of the upper edge 31. The recess 35 also forms a free space on the circumferential contour of the friction lining 4, through which the pressure means 7 can extend with at least a part of its cross section. For this purpose, the recess 35 is wider than the width B of the angled pressure element section.

The bottom of the recess 25 in the back plate 5 is deeper and thus arranged closer to the axis of rotation a than the sections 31a, 31b of the upper edge 31 of the friction plate 4 which directly adjoin the recess 35 formed in the friction plate 4 in the circumferential direction.

Thus, by means of said recess 25, a free space for traversing the pressure piece is provided. The pressure element thus occupies a portion of its length that is relatively low radially outward, which reduces the risk of structural tightness between the components of the disc brake and the wheel rotating about the brake, i.e. the risk of the brake components wearing internally on the rotating wheel.

According to fig. 6, on the back surface 17 of the back plate 9, below its upper edge 21, a boss 40 is integrally molded. The boss 40 is disposed closer to the edge 21 of the upper portion than the edge 22 of the lower portion of the back plate 5. The projections are arranged centrally along the axis of the brake lining 2, i.e. at the same distance towards both lateral edges 23a, 23 b. In order to support the projection on a correspondingly designed surface of the brake caliper 1, the projection is provided with at least one downwardly facing support surface 42 (fig. 4).

The boss 40 has a quadrangular plan view in a plan view from above. The two outer corners 41 of the projection 40, which are spaced apart from the rear face 17, are each rounded and are each rounded with a corner radius R of at least 4 mm. The rounding of the angle 41 has manufacturing advantages during the cutting process involving the corresponding recess 38 in the brake caliper 1 (fig. 5 b). The recess 38 serves as a lining receptacle in that it receives at least a part of a projection 40 of the brake lining and is provided for this purpose with a correspondingly rounded inner corner 39 having a corner radius of at least 4 mm.

A flat pressing surface 43, which has a width of 10 to 20mm and a length or depth of at least 7mm, is formed on the projection 40 facing away from the support surface 42. The pressing surface 43 is deeper and thus disposed closer to the rotation axis a than the recess 25. The pressure element 7 is supported on the brake lining only on the pressure surface 43, i.e. with the lower side of the meandering structure 11 of the following shorter longitudinal section 12, which forms the contact surface 12 a.

The longitudinal section 12 is at the same time the second end section 7c and thus also the end section of the pressure piece 7. The end face of which is opposite to the transverse wall of the brake caliper 1 which at least partially accommodates the boss 40.

A short transition surface 44 is connected to the pressure surface 43 for bearing against the pressure element 7 toward the friction lining 4. The transition surface 44 rises up to the bottom of the recess 25, for example in the form of a curve or alternatively an inclined ramp. The transition surface 44 intersects the bottom of the recess 25 at an edge 45, wherein according to fig. 4 the edge 45 is arranged in a plane of the back plate 5 between the plane of the fastening surface 16 and the plane of the back surface.

An edge region 47 is connected to the pressure surface 43 laterally, i.e., as viewed in the circumferential direction of the brake lining, and projects beyond the pressure surface 43. The end section 12 of the second end section 7c of the pressure piece 7, which end section is supported on the pressure surface 43, is therefore clamped by the two raised edge regions 47, so that the pressure piece 7 has no or only a small lateral play with respect to the brake lining 2.

When the bracket 60 is installed, it is not only the bearing element of the leaf spring 9, but it is also a locking element. The edge contour 64 of the web 9 then forms a stop which is not or only slightly spaced apart from the oppositely formed surface on the projection 40. This prevents the brake lining 2 from being lifted with its support surface from the brake caliper or only slightly. The locking effect is achieved by forming a groove 48 in each of the two edge regions 47 of the projection 40, which grooves form corresponding stops.

Viewed in the circumferential direction of the stop lining 3, the groove 48 is arranged in front of or behind the center of the back plate 5, the distance to the center being the same. Each groove 48 is connected along a respective side 49 of the boss 40. The bottom of each groove 48 faces the pin 13 and is situated at a small distance from the corresponding contour 64 of the bracket 60, or even there is a constant contact between said contour 64 and the bottom of the groove 48. However, if no continuous contact is present, the distance is always small and in particular smaller than the distance of the pin 13 from the meandering structure 11 or from the end section 12 of the pressure piece 7.

The contours 64 of the bracket 60, which serve as locking elements, thus each form a stop, and the grooves 48 of the brake lining 2 each form a counter stop. If the brake lining 2 jumps upwards as a result of a strong jerk, this will therefore also cause the pressure piece 7 to lift to the same extent, which movement is locked at the latest when the groove 48 touches the contour 64. This prevents the occurrence of larger movements which must be completely absorbed by the leaf spring 9 and thus extends the service life of the leaf spring 9.

The groove 48 may be designed to be open along one side thereof, that is to say towards the corresponding side 49 of the boss 40. The groove 48 may be open at its end facing away from the back plate 5. The grooves are oriented towards the back plate 5 with such a length that they extend not only over the depth of the lands 40, but also throughout the thickness of the back plate 5. The stop formed by the contour 64 of the side section 63 is thereby brought closer to the back plate 5. This minimizes or even avoids the tilting moment when the brake lining 3 comes into contact with it.

On the wheel inner side, the pressure element 7 is spaced apart from the leaf spring 9 only by a small distance, and one end 9a of the leaf spring 9 engages even in a form-locking manner in the U-shaped recess 7g of the first end section 7a of the pressure element 7. The insertion of the leaf spring 9 in the recess 7g is equivalent to the insertion of the hook in the holder.

The leaf spring 9 is supported with a spring section 9d, which is connected to the hook-shaped spring end 9a, on an upper inner surface 14b of the slot 14 facing away from the lining channel 6. As a result, the inner brake lining of the two brake linings can also be lifted only slightly from its radial support surface by the action of the pressure means 7.

Overall, it is achieved that 3 holds the two brake linings 2 radially to the disc brake caliper axis a by means of spring force and, in the event of lifting of one or both brake linings, the displacement associated therewith is tightly limited by the stop and the counter stop.

According to fig. 7 and 9, the pressure piece 7 is provided on its first end section 7a with two side sections 7k which extend the base 7d of the pressure piece 7 at an oblique angle, on each side of a recess 7g which is also provided in the first end section 7 a. The side sections 7k are located in the extension of the side edges 7e, 7f of the middle section 7b, which is designed as a groove, and have a bent, but in itself straight, profile, as viewed in the longitudinal direction of the pressure piece 7, relative to the middle section 7 b. The remaining part of the first end section 7a is also bent with respect to the middle section 7 b.

In order to adapt with low play to the opposite circular-arc-shaped rear wall 14a of the slot 14, the end side 7m forms the outermost end of the pressure piece 7, which extends over the respective circular arc 27 (fig. 7). The imaginary center of the circular arc 27 is located outside the pressure piece 7, i.e. above the intermediate section 7 b.

Fig. 11 and 12 show a further embodiment of the pressure piece 7. In this case, it can be advantageous with regard to its stability if the two side edges 7e, 7f are additionally elongated in such a way that they extend not only along the longer straight base edge 7d, but also along the first end section 7a which is arranged obliquely to the base edge.

In this respect, additional lateral sections can be used to laterally support the pressure means 7, which engage in the slot 14 of the brake caliper, on the brake caliper 1, as long as the inner width between the additional lateral sections is equal to or greater than the width of the slot 14.

Compared to the first embodiment of the pressure means, the side edges 7e, 7f are arranged steeper with respect to the base 7 d. Furthermore, fig. 11 shows that the height of the side edges 7e, 7f decreases towards the second end section 7 c. In this case, in particular in this part of the disc brake which is further outside the vehicle, there is in fact only a small distance to the surrounding vehicle, that is to say to the inside of the rim.

List of reference numerals

1 brake caliper

2 brake lining

3 brake lining

5 Back plate

5a stop

6 lining channel

7 pressing piece

7a first end section

7b middle section

7c second end section

7d bottom edge

7e side edge

7f side edge

7g recess

7k side section

7m end side

8 compress tightly subassembly

9 leaf spring

9a end of leaf spring

9b middle section

End of 9c leaf spring

9d spring section

9e bent part and bent part

9f bent part and bent part

10a form-locking element

10c form closure element

11 zigzag structure

11a bending part

11b bending part

11c straight extended section

11d pit

12 longitudinal section

12a contact surface

13 pin

13a axis

14 gap

14a rear wall

14b upper inner surface

14c lower inner surface

15 protrusion

16 fixed surface

17 back side

18 sides

21 upper edge

22 lower edge

23a side edge

23b side edge

25 recesses in the back plate

27 arc of circle

31 upper edge

31a section

31b section

33 recess

35 recesses in friction plates

38 recess in brake caliper

39 inner corner

40 boss

Corner part 41

42 bearing surface

43 pressing surface

44 transition surface

45 edge

47 edge region

48 grooves

Side face of 49

50 supporting block

60 bow, support element, locking element

61 opening

62 middle section

62a support

63 side section, contact piece

64 profile, stop

66 opening

Axis of A brake disk, axis of rotation

A1 distance

A2 distance

Axis of rotation of A3 disc cutter

Width B

F-shaped disc milling cutter

Length of L-terminal section

L1 longitudinal midline

Thickness of M material

Radius of R corner

Angle of W