EP3655676A1

EP3655676A1 - Disc brake with a tensioning device arranged therein and supporting roller for the tensioning device

Info

Publication number: EP3655676A1
Application number: EP18742699.4A
Authority: EP
Inventors: Thomas Klaas; Michael Pehle
Original assignee: BPW Bergische Achsen KG
Current assignee: BPW Bergische Achsen KG
Priority date: 2017-07-18
Filing date: 2018-07-05
Publication date: 2020-05-27
Also published as: ZA201908203B; CN110892168B; AU2018302088B2; RU2758923C2; CN110892168A; RU2020107100A3; US11624414B2; US20200232527A1; RU2020107100A; DE102017116112A1; WO2019015716A1; AU2018302088A1

Abstract

The invention proposes a disc brake having a brake caliper (1) and a tensioning device arranged therein for applying force to the brake linings of the disc brake, wherein part of the tensioning device is a brake lever (10) which can be actuated by a force element and preferably by a compressed air cylinder. The brake lever is composed of a lever arm (14), against which the force element is supported, and a brake application shaft (15), which is supported against a pressure piece (8) acting towards the brake linings, and is also supported from the inside against the brake caliper, wherein the brake caliper (1) and the brake application shaft (15) face each other and are formed as shells (21, 22) in which a supporting roller (20) with a roller axis (A) running transverse to the tensioning direction (Z) is mounted. To keep the mutual movability of the parts involved low by the simplest measures possible and without the need for additional parts, the supporting roller (20) is supported with the lateral surface (20A) thereof directly in one of the two shells (21, 22) and is designed to be non-rotatable or have only limited rotational movement with respect to this shell. The supporting roller (20) also serves as a means to centre the brake lever (10) laterally in the brake caliper. A supporting roller particularly suited to these purposes is also to be created.

Description

'Disc brake with arranged therein Zuspannvorrichtung and support roller for the

Clamping unit '

The invention relates to a disc brake with a caliper and an application device arranged therein according to the preamble of claims 1 and 1 1st

The invention further relates to a support roller for the application device of a disc brake.

Disc brakes are usually provided within their caliper with a brake application device. This transmits and possibly amplifies the force with which the brake pads arranged on both sides of the brake disc are brought into contact with the brake disc so as to achieve the braking effect by friction.

In generic disc brakes, which are often operated by compressed air, a component of the application device is a pivotably arranged in the brake caliper brake lever. The brake lever consists of a lever arm and a designed in cross-section as an eccentric Zuspannwelle. On the lever arm, the force member of the disc brake is supported, z. B. the air cylinder in the case of a pneumatically operated disc brake. The Zuspannwelle of the brake lever is supported on the one hand against an operating towards the vehicle interior brake pad working pressure piece, and on the other hand against the back of the caliper housing. From DE 195 15 063 C2 and DE 10 2012 006 089 A1 disc brakes are known, which have the aforementioned features, and in which the rear, ie brake caliper side support of the brake lever, an inner surface of the brake caliper on the one hand, and the application shaft of the brake lever on the other hand facing each other are formed as shells. In the shells, with a roller axis extending transversely to the application direction, a support roller is mounted. In the design according to DE 195 15 063 C2, the support roller is in one piece, while in the design according to DE 10 2012 006 089 A1 two separate support rollers are used, since the application shaft of the brake lever is divided into two with a first longitudinal section and a second longitudinal section between which there is a free space for the accommodation of an adjustment device. To center the support rollers in the direction of its roller axis relative to the brake lever, is on the Brake lever attached an additional, complex shaped sheet metal part. Tabs on the sheet metal part prevent the support rollers from shifting along their axis relative to the brake lever. The invention is based on the object, at a disc brake arranged in the brake caliper application device, which, inter alia, has a pivoting brake lever to keep the mutual mobility of the components involved low, through the simplest possible measures and without the need for additional components. Furthermore, a particularly suitable for this purpose support role is to be created.

To solve this problem, a disc brake with the features of claims 1 and 11, and a support roller for the application device of a disc brake with the features of claim 25 are proposed.

The disc brake is characterized in a first embodiment, characterized in that the support roller is supported with its lateral surface directly in one of the two shells and with respect to this shell rotationally fixed or limited rotationally movable. The disc brake is characterized in a second embodiment in that the support roller axially to its alignment with a first surface axially against the caliper, and with a second surface axially against the Zuspannwelle of the brake lever, wherein the second surface is opposite to the first surface aligned , A support roller according to the invention for the application device of a disc brake is characterized by a formed for supporting the support roller between two shells lateral surface and arranged at one end of the lateral surface collar which extends radially beyond the lateral surface out, wherein the support roller asymmetry with respect to has its roller axis, and the asymmetry in a parallel to the roller axis extending depression or flattening on the otherwise cylindrical surface is.

As a result of these measures, in the case of a disc brake with a brake application device which has a pivotable lever, the mutual mobility of the components involved, in particular the mutual mobility transversely to the application direction, can be kept low, by simple measures and without the necessity additional components. Various embodiments of the disc brake according to the invention and the support roller according to the invention are specified in the subclaims. According to one embodiment of the disc brake, the support roller is not rotatable or at most limited rotatably formed with respect to the shell formed on the clamping shaft. This is preferably achieved by virtue of the fact that the support roller for achieving the rotational strength or the rotation limitation has an asymmetry with respect to the roller axis. The asymmetry preferably exists in a recess extending parallel to the roller axis on the otherwise cylindrical circumferential surface of the support roller.

According to one embodiment, the shell formed directly on the application shaft of the brake lever is composed of two partially circularly curved segments of the same radius and a flattening arranged between the segments and extending parallel to the roller axis, the flattening projecting radially inwards relative to the radius of the segments. For example, the flattening may be designed as a shallow channel that forms the bottom of the shell. It is also proposed that the width of the flattening is less than the width of the depression on the lateral surface of the support roller, preferably 10% to 30% less.

In the second embodiment of the disc brake according to the invention, the support roller is axially against the brake caliper for its alignment in the axial direction with a first surface, and with a second surface axially against the application shaft of the brake lever. The second surface is oriented opposite the first surface, and preferably, the second surface is axially offset from the first surface.

The support rollers preferably present as a support roller pair are therefore not only support means in the transmission of the brake application forces, but they are also lateral alignment means which align the brake lever transversely to the application direction and so laterally center in the caliper housing.

For mutual alignment of the components involved is also proposed that the first surface is an end face of the support roller and bears against an arranged inside the caliper alignment surface. As an advantageous embodiment, it is proposed that the first surface is located at the end of a pin disposed on the support roller, which has a smaller diameter than the support roller on its shell surface mounted in the shells. Preferably, the alignment surface arranged inside the caliper is a plane-machined inner surface of the caliper whose surface normal coincides with the axis of rotation of the support roller.

Preferably, the support roller is provided with a collar which extends radially beyond the bearing in the shells lateral surface of the support roller out, wherein the second surface is located on the collar.

Because of the limited space inside the brake caliper, it may be advantageous if the federal government extends with the second surface formed thereon only over a partial circumference of the lateral surface of the support roller, namely on those part of circumference on which the federal government takes over the axial support. In this case, on the remainder of the circumference, a covenant is either not present, or only present in a radially reduced height.

Furthermore, it is proposed with respect to the support roller that its lateral surface on the part circumference, over which the collar extends, has an asymmetry with respect to the roller axis. The asymmetry is preferably a depression on the otherwise cylindrical lateral surface.

For mutual alignment of the components involved is also proposed that the second surface bears against a laterally arranged on the application shaft alignment surface. This alignment surface may have the shape of a planar-machined ring segment. In addition, if the axis of the ring segment coincides with the roller axis, the shell in question and the ring segment can be produced in a common milling or drilling process.

In principle, the support roller, which is preferably made of steel, can be a single support roller that runs through the length of the application shaft of the brake lever. However, a configuration using two support rollers is preferred. According to this embodiment, the brake caliper side bearing is divided into two with a first and a second shell, in each of which a support roller is mounted, wherein the caliper is provided between the two shells with a housing opening. The housing opening at this point of the caliper has several advantages. So can be through this housing opening Pass tool through which the internal processing takes place during the manufacture of the caliper. When the disc brake is ready for operation, the housing opening can serve to reset an adjuster of the disc brake arranged behind it, for B. after the replacement and insertion of new brake pads.

Preferably, the two support rollers are provided at their ends facing away from each other with an end face which rests against a disposed inside the caliper side alignment surface.

The support rollers can be supported directly on the formed on the back of the caliper shells. However, preference is given here to a type in which an additional bearing shell is arranged between the brake caliper-side shells and the support rollers. This has the advantage that when a wear on this bearing not the caliper needs to be renewed, but an exchange of additional bearing shells is sufficient.

In the design with two separate support rollers and the application shaft of the brake lever is divided into two with a first longitudinal portion which is disposed on one side of the plane of movement of the lever arm, and a second longitudinal portion spaced from the first longitudinal portion, which on the other side of the plane of movement of the lever arm is arranged. At each of these two longitudinal sections, a shell is formed, in which then each support roller directly, so without an additional bearing shell is supported.

It is advantageous for the design of the support roller, if this is provided following the collar with a pin which has a smaller diameter than the lateral surface of the support roller. The collar extends only over a partial circumference of the lateral surface, whereas on the remaining circumference a collar is not present or only in a radially reduced height. In this case, the lateral surface has the asymmetry on the part circumference over which the collar extends.

Further advantages and details will become apparent from the following description and with reference to the accompanying drawings. Show:

Fig. 1 in a side view of the caliper and the brake disc a

Commercial vehicle disc brake; 2 shows a longitudinal section through the designated in Figure 1 with II portion of the caliper. 3 is a perspective view of a support surface inside of the

Saddle rear wall of the caliper;

4 shows the support surface including a bearing shell placed there; 5 shows the groove-shaped bearing shell in perspective detail view;

6 shows a further longitudinal section through the saddle rear wall, the support surface and the bearing shell set thereon; Fig. 7 in an exploded view of the caliper, two support rollers and a

Brake lever of the disc brake;

FIG. 8 shows the objects according to FIG. 7 a slightly offset perspective; FIG. Fig. 9a shows a cross section through the support roller in the region of the system of the support roller against the brake lever, and

Fig. 9b, the objects of Fig. 9a in a changed rotational position of the support roller. In Fig. 1 and Fig. 2, a brake caliper 1 of a disc brake is reproduced, the disc brake is here of the design of a pneumatic-operated commercial vehicle brake Schiebesattel- or floating caliper type. The cast in a single piece caliper 1 is composed of three sections. A first saddle portion 11, which is inside the vehicle when the brake is mounted, is provided in its interior with a cavity 7, which provides space for a Bremszuspannvornchtung. A second saddle section 12, which is located outside the vehicle when the brake is mounted, is arranged on the opposite side of the brake disc 2 of the disc brake. The two saddle sections 11, 12 are connected to one another by a bridge section 13, which bridges the brake disk 2 and thereby provides a free space for at least part of the brake disk 2 and for the brake linings. The caliper 1 is here in one piece insofar as the two saddle sections 11, 12 and the bridge section 13 consist of a single part. The first saddle portion 1 1 is open to the free space of the bridge portion 13. This opening serves, inter alia, as a mounting opening and is so large that through them, the application device can be mounted. The opening is closed after completion of the brake assembly, by a lid.

Not graphically reproduced are the two brake pads of the disc brake. A first brake pad is located in Fig. 1 right of the brake disc 2. This application-side brake pad is actuated directly by the arranged in the cavity 7 of the saddle portion 11 application device and pressed against the brake disc 2. The second brake pad is disposed on the vehicle outer saddle portion 12, and there assumes a fixed position. He is the reaction-side brake pad. The task of the application device is to reinforce the braking forces generated by a force element and to transmit them in the application direction Z, which extends parallel to the axis of rotation of the brake disk 2.

Components of the application device are, inter alia, two rotatably supported against a saddle rear wall 18 support rollers 20, a pivotally mounted in the brake caliper housing brake lever 10 and in the direction of the vehicle interior, so zuspannseitigen brake pad working pressure piece. 8

The pressure piece 8 has the shape of a transverse to the application direction Z extending traverse. On the middle of the cross member 8, this is connected via a thread with a plunger, which is supported against the application-side brake pad, and this can act on the brake disc 2.

The pivotable brake lever 10 is fork-shaped and consists of a lever arm 14 and a split on two longitudinal sections Zuspannwelle 15. The application shaft 15 is supported on the one hand on the support rollers 20 against the saddle rear wall 18, which closes the cavity 7 facing away from the brake disc. As part of this support is between each of the two longitudinal sections of the application shaft 15 and a fixed inside the saddle rear wall 18 integrally formed shell 21 each one in the event of wear interchangeable bearing shell 19 is arranged. On the bearing shell 19, which is designed as well as the shell 21 as a part-cylindrical groove, the respective support roller 20 is supported rotatable. For this purpose, the support roller 20 is cylindrical over the major part of its circumference with a radius which is equal to the inner radius of the bearing shell 19th

In the other direction, ie in the application direction Z, the application shaft 15 is pivotally supported by a further pivot bearing 17 against the pressure piece 8. For this purpose, the pressure piece 8 has a supporting area in the form of a half shell. The further pivot bearing 17 is formed here as a rolling bearing.

To achieve a high clamping force, the application shaft 15 is mounted eccentrically. Because the supported against the caliper, defined by the axis A of the support rollers 20 pivot bearing is offset in height compared to the pivot axis of between the application shaft 15 and the thrust piece 8 arranged pivot bearing 17. With a rotation of the eccentrically contoured Zuspannwelle 15 therefore in the application direction Z to a forward movement of the pressure piece 8, whereby the brake is applied and exerts braking force.

This is formed near its free end with a Abstützort against which the force member of the disc brake works. In air-actuated disc brakes, this force member is a pneumatic brake cylinder, which is supplied by the compressed air system of the vehicle with compressed air.

The brake lever 10 is fork-shaped overall, since it branches, starting from the arranged on the pivot center line lever arm 14, in two legs. The first longitudinal section is located on the first leg, and the second longitudinal section of the application shaft 15 on the second leg. The brake lever 10 has a free space between these two longitudinal sections. This and further provided with a threaded hole center of the pressure pad 8 provide sufficient space for an adjustment. This is designed to compensate for the brake wear occurring over time and to correct the clearance of the brake. Components of the adjusting device include a drive element, a release of the brake reducing output element, a one-way clutch and an overload member. The output element of the adjusting device may be a spindle. This is provided with an external thread which is screwed into the threaded hole in the center of the pressure piece 8. Most of the parts of the adjusting device are arranged on a Nachstellachse. The Nachstellachse is located on the Zuspannachse Z and at the same time extends perpendicular to the plane in which the brake disc 2 extends. Since the application shaft 15 is divided into two longitudinal sections, two spatially separated, channel-shaped shells 22 for supporting one of the support rollers 20 are formed on the brake lever 10. Furthermore, the bearing shells 19 are also present twice.

The one shell 22 with its support roller 20 is located on one side, and the other shell 22 with its support roller 20 is located on the other side of that plane in which the lever arm 14 of the brake lever 10 executes its pivotal movement.

Between the other two, ie the shell 21 formed on the rear saddle wall 18 and preferably at the same time on the readjustment axis of the adjusting device, there is an opening 25 in the saddle rear wall 18. This provides space for a return element of a rear part device when the brake is ready for operation. Because the brake pads of the disc brake are worn, they must be replaced. Subsequently, the adjusting device must be returned to its initial position, which is done by means of the aforementioned rear sub-device. The restoring element of this rear part device is located in the opening 25 of the slender rear wall 18 and is provided with wrench flats to which a corresponding tool can be attached for re-dividing the brake.

The two shells 21 of the saddle rear wall 18 are designed for the purpose of conditioning the bearing shells 19, which are interchangeable when worn, each designed as a part-cylindrical groove. This simplifies the manufacturability of the shells 21, especially since the shells 21 are aligned with each other.

According to FIG. 4, for manufacturing reasons, each shell 21 is formed on a plateau cast on the saddle rear wall 18 inside. Each shell 21 is machined as shown in FIG. 3, resulting in a machined, trough-shaped surface of H-shape. Because this surface comprises two wider support surface sections and a narrower middle section arranged therebetween. The narrower middle section is due to two incisions with which the plateau is provided due to the casting process. In each cut a wing-shaped tab 19A of the bearing shell 19. The outer side of the bearing shell 19 extends in the circumferential direction, as the narrow center portion of the shell 21. In this way, the bearing shell 19 is possible to wander a little on the shell 21 in the circumferential direction , However, this possibility of movement is limited in both circumferential directions. Each bearing shell 19 is preferably made of an originally flat, produced by stamping and forming metal sheet with a sliding bearing coating. The part-cylindrical arched outside lies flat against the shell 21. On the part-cylindrical inside of the bearing shell 19, the support roller 20 rests with its cylindrical lateral surface 20A, so that the support roller 20 is freely rotatably supported about its roller axis A in the bearing shell 19.

On the other hand, as will be explained below with reference to FIGS. 9a, 9b, the support roller 20 can not rotate freely with respect to its other shell, ie, with respect to the shell 22 formed directly on the application shaft 15. Rather, here is a rotational mobility either not present or at least greatly reduced by the support roller 20 with respect to the shell 22 rotatably or limited rotatably formed. This is achieved by an asymmetry with respect to the roller axis A. This asymmetry consists in a flattening 27, which is parallel to the roller axis A, of the otherwise cylindrical outer surface 20A. This flattening 27 extends over the same axial length as the lateral surface 20A. The flattening 27 extends in the circumferential direction over an angle which is less than 80 °, whereas the remaining circumference is cylindrical.

Also, the surface of the shell 22 to which the support roller lies directly, is not exactly part-cylindrical and thus also asymmetric with respect to the axis A. Rather, the shell 22 is composed in the circumferential direction of two partially circular or partially cylindrical curved segments 31, 32 of Same radius R1 and the same reference point of these radii, and from a at the bottom of the shell 22 between the segments 31, 32 arranged flattening 33. The flattening 33 leads to the asymmetry and extends parallel to the roller axis A. The flattening 33 projects in comparison to the course of the segments 31, 32 radially inward by the radially measured distance A1 between the roller axis A and the flattening 33 is at least partially smaller than the radius R1 of the shell segments 31, 32. To the rotatability of the support roller 20 relative to the shell 22nd To limit narrow, the width B1 of the flat 33 in the shell 22 is less and preferably 10% to 30% low r as the width B2 of the flattening 33 with a small radial distance opposite flattening 27 on the support roller 20. Fig. 9b shows the situation in which the present in the transition between the cylindrical surface 20A and the flattening edge 27 against the flattening 33rd at the bottom of the shell 22. From reaching this rotational position of the support roller 20 is no further Rotation relative to the shell 22 more possible. Due to the flats 27, 33, the maximum possible angle of rotation in both directions of rotation is 6 ° in each case.

The radius R1 of the shell segments 31, 32 is slightly larger and in any case not smaller than the radius of the cylindrical part of the lateral surface 20A. The support roller 20 can therefore, in order to avoid too high and therefore expensive manufacturing precision in the surface processing of the parts, have some radial play in the shell 22. Nevertheless, due to the presence of the opposing depressions 27, 33, a good contact of the support roller 20 in the shell 22 is achieved.

The support roller 20 is ground so that the grooves on the cylindrical surface 20 A of the support roller in the circumferential direction. For a low wear on the surfaces may be advantageous if the segments 31, 32 are fixed with a rotating about the axis A grinding, milling or drilling tool, wherein the grooves produced thereby extend in the circumferential direction.

In FIGS. 7 and 8, before the final assembly, the two support rollers 20 and the brake lever 10 are shown. Each support roller 20 has three sections in its longitudinal direction, namely first the actual support section with the lateral surface 20A, secondly a subsequent collar 40 and thirdly a subsequent to the collar 40, the end of the support roller 20 forming pin portion 41. The collar 40 and the End of the support roller 20 are formed so that the support roller 20 abuts in the axial direction A with a first surface F1 against the caliper 1, and with a second surface F2 against the brake lever 10.

The second surface F2 is oriented opposite to the first surface F1. In addition, the second surface F2 is arranged offset in the axial direction A to the first surface F1. The first surface F1 is the free end face of the pin 41. This is designed flat and it is at best with little play a formed directly on the brake caliper 1 alignment surface 44 opposite. The two alignment surfaces 44 are mutually facing side surfaces inside the caliper 1, the surface normal with the axis A of the support rollers coincide. Both alignment surfaces 44 are machined flat, z. B. by grinding or milling.

Because of the limited space inside the brake caliper, the pin 41 has a smaller diameter than the support roller 20 on its in the shells 21, 22 mounted shell surface 20A. The collar 40 arranged between the lateral surface 20A and the pin 41 extends radially beyond the cylindrical lateral surface 20A of the support roller. In this way, one side of the collar 40 forms the second alignment surface F2. This surface F2 is located in the longitudinal direction of a roller formed directly on the brake lever 10 alignment surface 45 with at most little play. The surfaces F2 of the two support rollers 20 face each other.

On each side of the application shaft 15 is in each case one of the alignment surfaces 45. Each alignment surface 45 has the shape of a ring segment, which can be machined flat or plan. The reference axis of the ring segment falls, which is favorable in the production of the shell 22, with the roller axis A of the support roller together.

Thus, the two support rollers 20 are not only support means in the transmission of the brake clamping forces, but they are also lateral alignment, ie alignment transverse to the application direction Z. Because each support roller 20 rests with the surface F1 against the alignment surface 44 of the caliper 1, so that the Support roller 20 is laterally aligned or centered with respect to the caliper. At the same time, the second surface F2, which is arranged on the radially widened collar 40 of each support roller, rests against the alignment surface 45 on the respective side of the brake lever 10. In interaction thus the lateral alignment or centering of the brake lever 10 is achieved relative to the housing of the caliper 1. In this case, the first support roller 20 takes over the alignment of the brake lever 10 in one transverse direction, and the second support roller 20, the orientation of the brake lever 10 in the other, ie opposite transverse direction. So there are no additional elements or components required to center the brake lever 10 transverse to the application direction Z in the caliper 1. At the same time, the collar 40 prevents the respective support roller 20 from moving in the direction of the centrally located free space, which is located between the two longitudinal sections of the application shaft 15. Because in this space are components of the application device and / or the adjustment, with which no collision may occur.

The surface F2 is not over the entire circumference, but only on a peripheral segment against the brake lever 10. Therefore, it is not necessary for the federal government to cover the entire circumference. Rather, as shown in FIGS. 7 and 8, the collar 40 extends only over a partial circumference of the support roller 20, whereas on the remaining circumference a collar is not present or only in a radially reduced height. The support rollers 20 have on that part of the circumference on which the collar 40 is located with the surface F2, the asymmetry described, ie the depression or flattening 27. This ensures the concrete rotational position of the support roller 20 in the shell 22 and has structural advantages. Because in the two corresponding corner regions of the caliper 1, as can be seen, for example, Figures 3 and 4, very little space. A collar 40 surrounding the entire circumference of the support rollers 20 would run the risk of colliding with surfaces or shoulders inside the brake caliper 1.

LIST OF REFERENCE NUMBERS

caliper

brake disc

cavity

Pressure piece brake lever

saddle portion

bridge section

lever arm

application shaft

pivot bearing

Saddle back wall

bearing shell

A tab support roller

A lateral surface

Bowl

opening

Depression, flattening segment

segment

flattening

edge

Federation

spigot

alignment

Axle, roller axle A1 distance

B1 width

B2 width

F1 first surface

F2 second surface

R1 radius

W twist angle

Z Zuspannrichtung

Claims

claims

Proposed is a disc brake with a brake caliper (1) and a clamping device arranged therein for applying force to the brake pads of the disc brake, wherein part of the application device is a by a force member and preferably a compressed air cylinder operable brake lever (10) composed of a lever arm (14 ), against which the force member is supported, and a Zuspannwelle (15) which is supported on the one hand against a working towards the brake pads pressure piece (8), and on the other hand from the inside against the caliper by the caliper (1) and the Application shaft (15) facing each other as shells (21, 22) are formed, in which a support roller (20) with transverse to the application direction (Z) extending roller axis (A) is mounted, characterized in that the support roller (20) its lateral surface (20A) is supported directly in one of the two shells (21, 22) and in relation to this shell rotatably or limited rotatably designed.

Disc brake according to claim 1, characterized in that the support roller (20) with respect to the formed on the clamping shaft shell (22) rotatably or limited rotationally movable.

Disc brake according to claim 1 or 2, characterized in that the support roller (20) has an asymmetry with respect to the roller axis (A) for its rotational strength or rotation limitation.

Disc brake according to claim 3, characterized in that the asymmetry in a parallel to the roller axis (A) extending recess (27) on the otherwise cylindrical surface (20A) exists.

Disc brake according to claim 4, characterized in that the recess (27) extends over the same length as the lateral surface (20A).

Disc brake according to claim 4 or 5, characterized in that the recess (27) is designed as a flattening. Disc brake according to claim 4, 5 or 6, characterized in that the shell (22) is composed of two partial circular arcuate segments of the same radius (R1) and an arranged between the segments, parallel to the roller axis (A) extending flattening (33) which projects radially inwards relative to the radius (R1) of the segments (31, 32).

Disc brake according to claim 7, characterized in that the flattening (33) is designed as a channel.

Disc brake according to claim 7 or 8, characterized in that the width (B1) of the flattening (33) is less than the width (B2) of the recess (27) on the lateral surface (20A) of the support roller (20), preferably 10% to 30% less.

Disc brake according to one of claims 7 - 9, characterized in that the radius of the support roller (20) is at most equal to the radius (R1) of the segments.

Disc brake with a brake caliper (1) and a clamping device arranged therein for applying force to the brake pads of the disc brake, wherein part of the application device is an actuatable by a force member and preferably a pneumatic cylinder brake lever (10) composed of a lever arm (14), against the power member is supported, and a Zuspannwelle (15), on the one hand against a working towards the brake pads pressure piece (8), and on the other hand from the inside against the caliper (1) by the caliper (1) and the Application shaft (15) facing each other as shells (21, 22) are formed, in which a support roller (20) with transverse to the application direction (Z) extending roller axis (A) is mounted, characterized in that the support roller (20) their orientation in the axial direction (A) with a first surface (F1) axially against the caliper (1), and with a second surface (F2) axially against the application shaft (15) of the brake lever (10) is applied, wherein the second surface (F2) opposite to the first surface (F1) is aligned.

Disc brake according to claim 1 1, characterized in that the second surface (F2) in the axial direction (A) is offset from the first surface (F1). Disc brake according to claim 11 or 12, characterized in that the first surface (F1) is an end face of the support roller (20) and abuts against an inside arranged on the caliper alignment surface (44).

Disc brake according to claim 13, characterized in that the first surface (F1) is located at the end of a pin (41) arranged on the support roller (20), which has a smaller diameter than the support roller (20) on its in the shells (21 , 22) mounted lateral surface (20A).

Disc brake according to claim 13 or 14, characterized in that the alignment surface (44) is a plane-machined inner surface of the caliper (1) whose surface normal coincides with the roller axis (A).

Disc brake according to one of Claims 1 1 to 15, characterized in that the support roller (20) is provided with a collar (40) which extends radially beyond the lateral surface (20A) of the support roller (20A) mounted in the shells (21, 22) ) and that the second surface (F2) is on the collar (40).

Disc brake according to claim 16, characterized in that the collar (40) extends only over a partial circumference of the lateral surface (20A), and that on the remaining circumference a collar is not present or only in a radially reduced height.

Disc brake according to claim 17, characterized in that the lateral surface (20A) of the support roller (20) on the partial circumference, over which the collar (40) extends, has an asymmetry with respect to the roller axis (A), preferably a recess (27 ) on the otherwise cylindrical lateral surface (20A).

Disc brake according to one of claims 1 1 to 18, characterized in that the second surface (F2) abuts against a to the application shaft (15) laterally arranged alignment surface (45).

20. Disc brake according to claim 19, characterized in that the alignment surface (45) has the shape of a plan-machined ring segment, wherein the axis (A) of the ring segment preferably coincides with the roller axis. Disc brake according to one of the preceding claims, characterized in that the brake caliper side bearing is divided into two with a first and a second shell (21), in each of which a support roller (20) is mounted, and that the caliper between the two shells (21) a housing opening (25) is provided, preferably a in the application direction (Z) extending housing opening.

Disc brake according to claim 21, characterized in that the two support rollers (20) are provided at their opposite ends in each case with an end face (F1) which rests against an inside of the caliper (1) arranged lateral alignment surface (44).

Disc brake according to claim 21 or 22, characterized in that between the shells (21) and the support rollers (20) each have an additional bearing shell (19) is arranged.

Disc brake according to one of the preceding claims, characterized in that the application shaft (15) is divided into two with a first longitudinal section, which is arranged on one side of the plane of movement of the lever arm (14), and a second longitudinal section spaced from the first longitudinal section the other side of the plane of movement of the lever arm (14) is arranged, and in that at each of the two longitudinal sections a shell (22) is formed, in each of which a support roller (20) is directly supported.

Support roller (20) for the application device of a disc brake, with a lateral surface (20A) designed to support the support roller between two shells and a collar (40) arranged at one end of the lateral surface (20A) extending radially beyond the lateral surface (20A). extends, wherein the support roller (20) has an asymmetry with respect to its roller axis (A), and the asymmetry in a parallel to the roller axis (A) extending recess (27) on the otherwise cylindrical surface (20A) exists.

26. A support roller according to claim 25, characterized in that this is provided following the collar (40) with a pin (41) having a smaller diameter than the lateral surface (20A).

27. A support roller according to claim 25 or 26, characterized in that the collar (40) extends only over a partial circumference of the lateral surface (20A), and that on the remaining circumference of a collar is not present or only in a radially reduced height.

28. A support roller according to claim 27, characterized in that the lateral surface (20A) on that partial circumference, over which the collar (40) extends, the asymmetry.