阅读说明：本技术 用于商用车的盘式制动器 (Disk brake for a commercial vehicle ) 是由 R·菲舍尔 M·赛德尔 于 2018-04-11 设计创作，主要内容包括：本发明涉及一种用于商用车的盘式制动器,该盘式制动器包括：制动钳(2),其包围制动盘(3)并且通过两个紧固件相对于制动盘(3)可轴向移动地固定在位置固定的制动器支架(1)上,紧固件分别具有与制动器支架(1)固定连接的引导横梁(9),为了制动钳(2)的轴向可移动性其中一个引导横梁作为固定轴承(4)被引导并且另外一个引导横梁在构成为具有浮动轴承轴线(5a)的浮动轴承(5)的滑动轴承中被引导,至少浮动轴承(5)具有包围引导横梁(9)的且不可移动地保持在制动钳(2)的制动钳孔(21)中的引导套(7),其中至少在引导横梁(9)的背对制动盘的端部区域上设置将引导横梁相对于环境密封的第一管状的长度可变的密封件,该密封件一方面固定在引导横梁(9)上并且另外一方面固定在引导套(7)中,第一管状的长度可变的密封件借助于压入引导横梁(9)中的盖(20)夹紧在引导横梁(9)上,第一管状的长度可变的密封件具有环形区段(12g),该环形区段嵌入在位于覆盖区段(9h,20b)、颈圈(20a)和环绕的外表面(20d)的一个区段之间的环绕凹槽(9e,20c)中,其中环形区段(12g)被外表面(20d)的该区段参照浮动轴承轴线(5a)径向向内固定地保持,并且环形区段(12g)被覆盖区段(9h,20b)参照浮动轴承轴线(5a)径向向外固定地保持。(The invention relates to a disc brake for a commercial vehicle, comprising: brake caliper (2) which surrounds a brake disk (3) and is fixed in a position-fixed brake carrier (1) in an axially displaceable manner relative to the brake disk (3) by means of two fastening elements, each having a guide cross member (9) which is fixedly connected to the brake carrier (1), wherein one of the guide cross members is guided as a fixed bearing (4) and the other guide cross member is guided in a plain bearing which is designed as a floating bearing (5) having a floating bearing axis (5a) for the axial displaceability of the brake caliper (2), wherein at least the floating bearing (5) has a guide sleeve (7) which surrounds the guide cross member (9) and is held immovably in a caliper opening (21) of the brake caliper (2), wherein at least on an end region of the guide cross member (9) facing away from the brake disk a first tubular sealing element of variable length is provided which seals the guide cross member against the environment, the seal is fastened on the one hand on the guide cross member (9) and on the other hand in the guide sleeve (7), the first tubular variable-length seal being clamped on the guide cross member (9) by means of a cover (20) pressed into the guide cross member (9), the first tubular variable-length seal having an annular section (12g) which engages in a circumferential groove (9e, 20c) between the cover section (9h,20b), the collar (20a) and a section of the circumferential outer surface (20d), wherein the annular section (12g) is held fixedly radially inwardly with reference to the floating bearing axis (5a) by the section of the outer surface (20d), and the annular section (12g) is held fixedly radially outwardly with reference to the floating bearing axis (5a) by the cover section (9h,20 b).)

1. A disc brake for a commercial vehicle, the disc brake comprising: brake caliper (2) which surrounds a brake disk (3) and is fixed in a position-fixed brake carrier (1) so as to be axially displaceable relative to the brake disk (3) by means of two fastening elements, each having a guide cross member (9) which is fixedly connected to the brake carrier (1), wherein one of the guide cross members is guided as a fixed bearing (4) and the other guide cross member is guided in a plain bearing which is designed as a floating bearing (5) having a floating bearing axis (5a) for the axial displaceability of the brake caliper (2), wherein at least the floating bearing (5) has a guide sleeve (7) which surrounds the guide cross member (9) and is held immovably in a caliper opening (21) of the brake caliper (2), wherein at least in the end region of the guide cross member (9) facing away from the brake disk (3) a first tubular sealing element of variable length is provided which seals the guide cross member against the environment, the seal is fixed on the one hand on the guide cross member (9) and on the other hand in the guide sleeve (7), the first tubular length-variable seal is clamped to the guide cross member (9) by means of a cover (20) pressed into the guide cross member (9), characterized in that the first tubular variable-length seal has an annular section (12g), the ring-shaped section is embedded in a surrounding groove (9e, 20c) between the covering section (9h,20b), the collar (20a) and a section of the surrounding outer surface (20d), wherein the annular section (12g) is fixedly held radially inwardly with reference to the floating bearing axis (5a) by the section of the outer surface (20d), and the annular section (12g) is fixedly held radially outwards with reference to the floating bearing axis (5a) by the covered section (9h,20 b).

2. The disc brake of claim 1, characterized in that the collar (20a) is integrally formed on the end of the cover (20) facing away from the brake disc (3) and the outer surface (20d) is a surrounding outer surface (20d) of the cylindrical body of the cover (20).

3. The disc brake of claim 2, characterized in that the annular section (12g) directly and/or indirectly contacts the outer surface (20d) and the cover section (9h,20b), respectively.

4. The disc brake of claim 3, characterized in that the annular section (12g) is held fixedly with radial pretension in a circumferential groove (9e, 20c) between the covering section (20b), the collar (20a) and the section of the outer surface (20 d).

5. The disc brake of any one of claims 2 to 4, characterized in that the annular section (12g) constitutes a pressure-tight seal in the surrounding groove (9e, 20c) relative to the cover (20).

6. The disc brake of any one of claims 2 to 5, characterized in that the annular section (12g) of the first tubular variable-length seal has a circular cross-section.

7. The disc brake of any one of claims 2 to 6, characterized in that a circumferential groove (9e) is molded into the end side of the end region of the guide cross member (9) facing away from the brake disc (3) and is defined radially outward with reference to the floating bearing axis (5a) by a cover section (9e) as a section of the end section (9b) of the guide cross member (9), and the cover section (9e) extends axially parallel to the floating bearing axis (5 a).

8. The disc brake of claim 7, characterized in that the ring segment (12g) is axially prestressed directly or indirectly against the guide cross member (9) in the circumferential groove (9 e).

9. The disc brake of any one of claims 2 to 6, characterized in that the encircling groove (20c) is configured as an annular groove between the underside of the covering section (20b), the inner side of the collar (20a) and the outer surface (20d), the covering section (20b) being attached on a radially outer end of the collar (20a) of the cover (20) and extending axially parallel to the floating bearing axis (5a) towards the brake disc (3).

10. The disc brake of claim 9, characterized in that the annular section (12g) is pretensioned by circumferential compression in a circumferential groove (20c) between the sections of the outer surface (20d) of the cover section (20b), the collar (20a) and the cover (20).

11. The disc brake of claim 10, characterized in that the annular segment (12g) is wrapped in the groove (20c) of the cover (20) by the collar (20a) and the covering segment (20b) of the cover in an angular range of 160 ° to 190 °, wherein the outer surface of the annular segment (12g) is in direct or indirect contact with at least the outer surface (20d) of the cover (20) and with the inside of the covering segment (20b) of the cover (20).

12. The disc brake of any one of claims 9 to 11, characterized in that the ring segment (12g) is axially prestressed directly or indirectly against the guide cross member (9) in the encircling groove (20 c).

13. The disc brake of claim 12, characterized in that the annular section (12g) is connected axially to a circumferential web (12e) which is in contact with a circumferential end face (9e) of the guide cross member (9).

14. The disc brake of claim 13, characterized in that the connection between the webs (12e) and the ring segments (12g) is provided with a waist (12 f).

15. The disc brake of claim 13 or 14, characterized in that the first tubular variable-length seal is attached to the ring section (12g) and the webs (12e) via a connecting section (12d), which connecting section (12d) constitutes a hinge function between the tubular variable-length seal and the ring section (12g) and the webs (12 e).

16. The disc brake of any one of the preceding claims, characterized in that the guide sleeve (7) has an elastic inner sleeve (11).

17. The disc brake of claim 16, characterized in that the first tubular, variable-length seal is connected with the inner sleeve (11).

18. The disc brake of claim 16 or 17, characterized in that the first tubular, variable-length seal is constructed in one piece with the inner sleeve (11).

19. The disc brake of any one of the preceding claims, characterized in that the first tubular, variable-length seal is designed as a diaphragm air spring (12).

20. The disc brake of any one of the preceding claims, characterized in that a second tubular variable-length seal is connected on the side of the guide sleeve (7) opposite the first tubular variable-length seal, which second tubular variable-length seal is connected on the other side to the guide cross-member (9).

21. The disc brake of claim 20, characterized in that the second tubular, variable-length seal is fixed on a stop ring (15) which is connected, preferably locked, to the guide sleeve (7).

22. the disc brake of claim 20 or 21, characterized in that the second tubular variable-length seal has a flange (17) on its edge facing away from the stop ring (15), which flange is inserted into an annular groove (18) of the guide cross member (9) and is held in the annular groove (18) by a retaining ring (16) fixed in the brake caliper (2).

23. The disc brake of any one of claims 20 to 22, characterized in that the stop ring (15) has a circumferential groove (15b) with a seal (22) on its outer surface.

24. The disc brake of claim 23, characterized in that the seal (22) has at least one double sealing lip.

25. The disc brake of claim 24, characterized in that the seal (22) is integrated as at least one double sealing lip in a groove (15b) on the stop ring (15).

26. The disc brake of one of claims 20 to 25, characterized in that the second tubular variable-length seal is designed as a second diaphragm air spring (14).

Technical Field

The invention relates to a disc brake for a commercial vehicle according to the preamble of claim 1.

Background

Such disc brakes are used in particular in heavy commercial vehicles. In this case, a brake caliper known under the name sliding brake caliper is connected to a vehicle-side brake carrier by means of fasteners.

The guide cross-member of the fastening element is usually connected to the brake carrier by means of a screw, wherein the guide cross-member is guided in a slide bearing of the brake caliper such that an axial displacement of the reference brake disk relative to the stationary brake carrier can be achieved.

The sliding guide system of the brake caliper consists of a main guide bearing and a so-called compensation bearing. The purpose of the sliding guide system is to keep the caliper against external forces (e.g. due to the presence of vibration stresses), to achieve an accurate and play-free positioning and to ensure a smooth movability in brake application and wear adjustment.

Basically the main guide bearing is realised to ensure movability, whereas the "holding" and "positioning" tasks are performed jointly by the main guide bearing and the compensation bearing. When the main guide bearing is equipped with a narrow clearance, the compensating bearing must have an increased clearance, or the possibility of elastic compensation, at least in the circumferential direction, to compensate for distance tolerances and bearing distance variations caused by operation.

In order to achieve a defined function, the compensating bearing (hereinafter referred to as floating bearing) is a guide sleeve which surrounds the guide cross member and is connected immovably to the brake caliper, and has an elastic inner sleeve made of an elastomer. The elasticity of the inner sleeve prevents rattling which may occur due to tolerances in the compensating bearing associated with this example. Another advantage of the elastic inner sleeve is low cost, high durability and ease of installation.

DE102012021690a1 describes a disc brake for commercial vehicles, which comprises a brake caliper surrounding a brake disc, which brake caliper is attached to a stationary brake carrier by means of two fasteners which are axially displaceable relative to the brake disc. Fig. 7 and 8 show the floating bearing in different positions in a sectional view (fig. 7 for a new brake lining, fig. 8 for a worn brake lining). The fastener of the floating bearing has a guide cross beam 9 fixedly connected to the brake bracket 1. The guide cross member 9 is fastened to the brake carrier 1 by means of a cap screw 10 having a head 19, which is surrounded by a guide sleeve 7 having an elastic inner sleeve 11 in an outer sleeve 13, which is held immovably in a caliper bore 21 of the caliper 2. At the end of the guide cross member 9 facing away from the brake disk, a first diaphragm air spring 12 is arranged, which seals the guide cross member from the surroundings and is fastened on the one hand to the guide cross member 9 and on the other hand in the guide sleeve 7. The first diaphragm air spring 12 is also mounted in a clamping manner on the guide cross member 9 by means of a cover 20 pressed into the guide cross member.

The floating bearing also has, in the region of the guide cross member 9 facing the brake disk, a second diaphragm air spring 14, a stop ring 15, a retaining ring 16, which has a flange 17 arranged in an annular groove 18 of the guide cross member 9. The second diaphragm air spring 14 is connected to the inner sleeve 11 and the outer sleeve 13 via a stop ring 15, wherein the stop ring 15 is mounted on the inner sleeve 11 via a locking lug 23/locking recess 24. At the connection between the second diaphragm air spring 14 and the stop ring 15, a sealing lip 22 is integrally formed on the end of the second diaphragm air spring 14, which sealing lip rests on the guide cross member 9.

a detailed description can be found in DE102012021690a 1.

These elastomer compensating bearings do not use a fixed package and are sufficient for normal use. However, when used with vehicles traveling on unpaved or heavily soiled roads, as well as with vehicles used on construction sites and off-road vehicles, the pressure of debris and dirt can damage the seals, allowing dirty water to enter the guide areas of the bearing bushes. Such consequences can lead to significant bearing wear and premature bearing bushing replacement.

As further compensation bearings, DU bearings with double-sided sealing have proven to be advantageous. In both designs, the open end must be sealed with an additional member. This requires additional handling and assembly on the caliper and is therefore costly. Furthermore, DU bearings are prone to noise generation during operation, which requires additional damping measures.

In any case, the open end, i.e. the end region facing away from the brake disk, must be sealed with additional components, which is achieved in the disk brake disclosed in DE102006050647a1 by a cover which is arranged in conjunction with the brake caliper and which covers the end-side outer circumferential region and the end side of the guide cross member.

However, additional handling of the caliper and assembly of the cover are required, resulting in corresponding additional costs.

DE19636942C5 describes a sliding caliper disc brake, the caliper of which is movably guided on a guide pin, wherein the guide pin extends through a through-hole of the caliper and projects with its free end from the through-hole, and a tubular, variable-length seal is provided, which seals off on one side the annular space between the inner wall of the through-hole and the guide pin, and which is held on the one hand on the caliper and on the other hand on the free end of the guide pin. The seal engages the free end of the guide pin with the end section from behind. A retaining device is provided which, together with the end face of the free end of the guide pin, forms an annular profile which is U-shaped in cross section for retaining the end section of the seal. The retaining means is in the form of a plug provided with a radial flange, which plug is retained in the end-side recess of the guide pin, and the end section of the seal abuts against the outer circumferential surface of the plug.

Disclosure of Invention

The object of the invention is to improve a disc brake of the same type such that its life is extended and its manufacturing costs are reduced by simple constructional measures.

This object is achieved by a disc brake having the features of claim 1.

The pressure-tight encapsulation of the floating bearing of the disc brake with respect to the environment and thus with respect to the influencing factors caused by driving can thus be achieved without any special handling of the brake caliper.

In particular when the new disc brake is used in a commercial vehicle exposed to increased risk of debris and contamination, the service life of the disc brake is extended by the invention to the extent that it is influenced by the fastening.

Another advantage is that the pressure-tight encapsulation allows the bearing to withstand cleaning of the brake by high pressure cleaning agents.

The radial and axial installation space and the function of the previous bearings can be maintained.

According to the invention, a double-sided diaphragm air spring is provided with internally and externally pressed and protected sealing elements on the side facing the brake disk and the side facing away from the brake disk. In addition, the central inner region of the bearing is provided with a sealing element which is compressed and protected on both sides.

The radial installation space inside the HNBR elastomer sleeve is used unchanged by the external membrane air spring, while the axial installation space is maintained in the state of new brake linings and worn brake linings: the bearing is located deeper within the bore by the amount of axially connected sealing annular sections (O-rings).

The disc brake for a commercial vehicle according to the invention comprises: a brake caliper which surrounds the brake disk and is fixed in an axially displaceable manner relative to the brake disk on a stationary brake carrier by means of two fastening elements, each having a guide cross member which is fixedly connected to the brake carrier, one guide cross member being guided as a fixed bearing and the other guide cross member being guided in a slide bearing which is designed as a floating bearing having a floating bearing axis for the axial displaceability of the brake caliper, at least the floating bearing having a guide sleeve which surrounds the guide cross member and is held immovably in a brake caliper opening of the brake caliper, wherein at least on the end region of the guide cross member facing away from the brake disk a first tubular variable-length seal is provided which seals the guide cross member from the environment, which seal is fixed on the one hand on the guide cross member and on the other hand in the guide sleeve, which seal is clamped on the guide cross member by means of a cover which is pressed into the guide cross member, the first tubular variable-length seal has an annular section which engages in a circumferential groove between the cover section, the collar and a section of the circumferential outer surface, wherein the annular section is held fixed radially inward with reference to the floating bearing axis by the section of the outer surface and the annular section is held fixed radially outward with reference to the floating bearing axis by the cover section.

One embodiment provides that the collar is integrally formed on the end of the cover facing away from the brake disk and that the outer surface is a surrounding outer surface of the cylindrical body of the cover. This allows a compact structure and simple assembly.

In one embodiment, the annular section directly and/or indirectly contacts the outer surface and the footprint section, respectively. This not only achieves a sealing abutment of the ring segments, but also a secure hold is easily achieved.

The advantage of an improved support and sealing of the annular portion with respect to the cover is achieved when the annular portion is held fixedly in a radially prestressed manner in the circumferential groove between the cover portion, the collar and the portion of the outer surface.

In a further embodiment, the annular section forms a pressure-tight seal in the circumferential groove relative to the cover. This is particularly advantageous as it enables a pressure-tight encapsulation with a high IP protection rating, preventing the penetration of high-pressure water, such as during high-pressure cleaning, and thus extending the service life of the floating bearing by reducing corrosion. Meanwhile, the guide beam may be made of conventional steel material, not stainless steel.

In one embodiment, the annular section of the first tubular variable-length seal has a circular cross section, since this can be produced simply with simple tools and has a good sealing effect, for example, when pressed.

One embodiment provides that the circumferential groove is formed into the end face of the end region of the guide cross member facing away from the brake disk and is delimited radially outward with respect to the floating bearing axis by a cover section as a section of the end section of the guide cross member, and the cover section extends axially parallel to the floating bearing axis. This is a compact and simple construction.

In this case, it is advantageous if the ring segment is axially directly or indirectly prestressed in the circumferential groove against the guide cross member, since this achieves a secure hold.

In an alternative embodiment, the encircling groove is configured as an annular groove between the underside of the covering section, the inner side and the outer surface of the collar, the covering section being attached on the radially outer end of the collar of the cover and extending axially parallel to the floating bearing axis towards the brake disc. This is advantageous for a compact construction.

In a further embodiment, it is provided that the annular section is prestressed by circumferential compression in a circumferential groove between the covering section, the collar and the section of the outer surface of the cover. This can be achieved in a simple manner and at low cost.

Here, in a further embodiment, the ring segment is wrapped in the groove of the lid by the collar and the covering segment of the lid in an angular range of 160 ° to 190 °, wherein the outer surface of the ring segment is in direct or indirect contact with at least the outer surface of the lid and with the inner side of the covering segment of the lid. In this way, additional mechanical protection can advantageously be formed.

In a further embodiment, the ring segment is axially prestressed directly or indirectly in the circumferential groove relative to the guide cross member. This results in an advantageous simple and effective fixing and sealing.

In a further embodiment, it is provided that the annular section is connected axially to a circumferential web, which is in contact with a circumferential end face of the guide cross member. The webs contribute to the support on the guide cross member, thus facilitating the assembly of the cover.

If a web is provided at the connection between the web and the ring section, it is advantageous to specifically control the rolling movement of the first diaphragm air spring.

In a further embodiment, it is provided that the first tubular variable-length seal is attached to the ring section and to the web via a connecting section which forms a hinge function between the tubular variable-length seal and the ring section and the web. This results in an advantageously simple and compact design.

In one embodiment, the guide sleeve has a resilient inner sleeve. This makes it easy to compensate for the tolerance difference.

For a compact construction and a simplified assembly, in one embodiment the first tubular variable length seal may be connected with the inner sleeve, wherein in an alternative embodiment the first tubular variable length seal and the inner sleeve may be integrally formed.

In a further embodiment, it is provided that the first tubular, variable-length seal is designed as a diaphragm air spring, so that an advantageously compact design is achieved.

A second tubular length-variable seal is connected to the guide sleeve on the side opposite the first tubular length-variable seal, and is connected to the guide cross-member on the other side, so that a further advantageous seal is achieved. Therefore, the pressure-tight encapsulation of the bearing can be easily achieved.

In one embodiment, the second tubular variable-length seal is fixed to a stop ring, which is connected, preferably locked, to the guide sleeve. This is advantageous for a compact structure and simple assembly.

In order to provide an advantageous seal, the second tubular variable-length seal has a flange on its edge facing away from the stop ring, which flange is inserted into the annular groove of the guide cross member and is held in the annular groove by a retaining ring fixed in the brake caliper.

In a further embodiment, the stop ring has a circumferential groove with a seal on its outer surface. This is advantageous because the stop ring thus has multiple functions, namely the connection, the sealing in the component.

If the seal has at least one double sealing lip, a favorable sealing effect can be achieved in the associated bore.

Alternatively, the seal is integrally formed as at least one double sealing lip in a groove on the stop ring, resulting in a particularly compact design.

In a further embodiment, the second tubular variable-length seal is designed as a second diaphragm air spring. This results in a compact and simple construction.

The following advantages arise:

1. The outer (first) membrane air spring is pressure-tightly sealed by an annular section shaped as an O-ring in the annular groove of the cover and sealed by compression on both sides, with the cover providing additional shielding and controlling the rolling movement.

2. The inner (second) membrane air spring is pressure-tightly sealed in the annular groove of the injection-molded stop ring by an integrally molded/injection-molded double sealing lip and sealed by being pressed into the hole in the protected position.

3. The inner (second) membrane air spring is pressure-tightly encapsulated by an injection-molded flange or square ring and is sealed in the protected position by a retaining ring or support ring pressed into an annular groove of the guide cross member.

4. Assembly is simplified by the support of the injection-molded tabs on the annular section (O-ring).

5. thus also enabling automatic assembly.

6. Modifications may be made.

7. the bare lid provides impact protection when new.

8. The customer-side space requirement is met by the outer edge of the cover when newly installed and by the outer edge of the first diaphragm air spring in the worn state.

9. The additional sealing element/structure also allows a so-called modular design with all advantages.

10. Since the guide beams are pressure-tightly encapsulated, guide beams made of conventional steel, rather than stainless steel, can be used, which has cost advantages in terms of material and processing.

Further advantageous embodiments of the invention are characterized in the dependent claims.

Drawings

Embodiments of the invention are described below with the aid of the figures. In the drawings:

Fig. 1 shows a schematic top view of a disc brake according to the invention in an unworn state, with a floating bearing shown partly in section;

FIG. 2 is an enlarged schematic cross-sectional view of the floating bearing according to reference II of FIG. 1 in a first position;

3-3a are enlarged schematic cross-sectional views according to the reference III of FIG. 2;

FIG. 4 is a schematic top view of the disc brake according to FIG. 1 in a worn state;

FIG. 5 is an enlarged schematic cross-sectional view of the floating bearing according to reference V of FIG. 4 in a second position;

Fig. 6 is an enlarged schematic sectional view of the marking VI according to fig. 5;

FIG. 6a is an enlarged schematic cross-sectional view of another embodiment in an unworn condition; and

Fig. 7 and 8 are schematic cross-sectional views of floating bearings in different positions according to the prior art.

Detailed Description

Fig. 1 shows a schematic plan view of a disc brake SB according to the invention in the unworn state and in a partial sectional view a floating bearing 5. Fig. 2 shows a schematic enlarged sectional view of the floating bearing 5 according to reference II of fig. 1 in a first position. Fig. 3 shows an enlarged schematic sectional view of the marking III according to fig. 2.

In this example, the disc brake SB is provided for a commercial vehicle and comprises a brake carrier 1, a brake caliper 2, a brake disc 3 with a brake disc axis of rotation 3a and brake linings 6, 6'.

the brake disk 3 is only symbolically represented here by a center line, which extends in the center plane of the brake disk 3.

The brake carrier 1 is mounted in a stationary manner on a vehicle equipped with a disc brake SB. The brake caliper 2 comprises a brake application section 2a having two bearing sections 2b, 2c and a caliper back 2d connected to the brake application section 2 a. The brake disc 3 is bridged by the caliper 2 so that the brake disc is arranged between the brake application section 2a and the caliper back 2 d.

On both sides of the brake disk 3, a brake lining 6, 6' is arranged in the brake carrier 1. The brake lining 6 arranged on the side of the brake disc 3 facing the brake application section 2a of the brake caliper 2 is referred to as a brake application side brake lining 6. The other brake lining 6 'is referred to as rear brake lining 6' with reference to the caliper rear 2d of the brake caliper 2.

The brake caliper 2 is mounted on the brake carrier 1 so as to be axially displaceable relative to the brake disc 3 in the direction of the brake disc axis of rotation 3 a. For this purpose, two fastening elements are provided, one of which forms a fixed bearing 4 with a fixed bearing axis 4a and the other forms a floating bearing 5 with a floating bearing axis 5 a. The fixed bearing axis 4a and the floating bearing axis 5a extend parallel to each other and to the brake disc rotation axis 3 a.

The floating bearing 5 comprises a guide sleeve 7, a guide cross member 9, a cap screw 10 with a head 19, an inner sleeve 11, a first tubular variable-length seal, which is designed here as a first membrane air spring 12 (outer membrane air spring 12), an outer sleeve 13, a second tubular variable-length seal, which is designed here as a second membrane air spring 14 (inner membrane air spring 14), a stop ring 15 and a retaining ring 16.

The floating bearing 5 is referred to herein as a so-called double-diaphragm air spring bearing.

The guide cross member 9 is fixedly connected to the brake carrier 1 by means of a cap screw 10, which cap screw 10 passes through a central hole 9a in the guide cross member 9.

The brake caliper 2 has a bearing section 2b, 2c on each side of the brake application section 2 a. One bearing section 2b receives a fixed bearing 4, while the other bearing section 2c is provided with a floating bearing 5. The guide sleeve 7 of the floating bearing 5 is held immovably in the further bearing section 2c, the brake caliper 2 being mounted displaceably on a guide cross member 9.

In the exemplary embodiment shown, the guide sleeve 7 has a resilient inner sleeve 11 and a metallic outer sleeve 13 surrounding the inner sleeve, which is pressed into the caliper opening 21 of the further bearing section 2c of the brake caliper 2. In a further embodiment, not shown, the guide sleeve 7 has only an outer sleeve 11, without an elastic inner sleeve 11, wherein the outer sleeve 11 is pushed with its inner bore directly onto the guide cross member 9 and can have a correspondingly thicker wall thickness.

The inner sleeve 11 is made of plastic, preferably an elastomer such as HNBR, and is injection moulded onto the inner wall of the outer sleeve 13. The inner sleeve 11 is supported on the inside on the guide cross member 9.

A first diaphragm air spring 12 is arranged on one end section 9b of the guide cross member 9 facing away from the brake disk 3, which seals the guide cross member 9 from the surroundings. The first diaphragm air spring 12 is fastened on the one hand to the guide cross member 9 and on the other hand to the guide sleeve 7.

The fastening of the first diaphragm air spring 12 to the guide sleeve 7 can be effected directly on the guide sleeve 7 and/or on the inner sleeve 11 (if an inner sleeve is present). As is realized in the exemplary embodiment shown here, the first diaphragm air spring 12 can also be formed integrally with the inner sleeve 11, i.e. it is made of the same material and forms an extension of the inner sleeve, which extends over the end section 9b of the guide cross member 9. In order to fix the first diaphragm air spring 12 on the guide cross member 9, the free end of the first diaphragm air spring 12 is clamped by means of a cover 20, which covers the head 19 of the cap screw 10 and is pressed into the end face in the head hole 9d of the guide cross member 9. This will now be described in detail.

In contrast to the prior art described in detail in DE102012021690a1 and according to fig. 7 and 8, the first diaphragm air spring 12 here comprises diaphragm air spring sections 12a, 12b and 12c, a connecting section 12d, a web 12e and an annular section 12 g.

The end 13a of the outer sleeve 13 facing away from the brake disk 3 bears axially against a shoulder 13a of the inner sleeve 13. One end 13b of the outer sleeve 13 facing the brake disc 3 is in contact with the stop ring 15.

Another difference with the above-mentioned prior art is that the cover 20 not only has a collar 20a, which is integrally molded on the end of the cylindrical body of the cover 20 facing away from the brake disc 3, but also comprises a surrounding footprint section 20b, which is attached on the outer radial end of the collar 20a and extends in the axial direction substantially parallel to the floating bearing axis 5a towards the brake disc 3. A recess 20c is formed between the underside of the covering section 20b, the inner side of the collar 20a and the surrounding outer surface 20d of the cylindrical body of the cap 20.

Fig. 2 and 3 show a position of the floating bearing 5 in which the brake linings 6, 6' of the disk brake SB are new and have not yet worn out. In this case, the first diaphragm air spring section 12a of the first diaphragm air spring 12 is arranged above the end section 9b of the guide cross member 9. The first diaphragm air spring section 12a is connected to a third diaphragm air spring section 12c, which is bent by about 90 ° relative to the floating bearing axis 5a in this position, by a second diaphragm air spring section 12b, which extends radially relative to the floating bearing axis 5a and merges into the radially outer end of the connecting section 12 d.

The connecting section 12d is itself connected at its inner radial end to a circumferential web 12e, the connecting section 12d providing a hinge function between the tubular variable-length seal (i.e. the first diaphragm air spring 12), the annular section 12g and the web 12 e. This is clearly shown in figures 5 and 6.

The webs 12e extend in the axial direction substantially parallel to the floating bearing axis 5a in the section facing the brake disk 3 and in the opposite axial direction. The section of the web 12e facing the brake disk 3 is in contact with the circumferential end face 9c of the guide cross member 9.

The other section of the web 12e facing away from the brake disk 3 is connected to the annular section 12 g. This connection between the tab 12e and the annular section 12g is provided with a waist-binding portion 12 f. In this way, the annular section 12g is axially connected to the tab 12 e.

Fig. 3a shows a further schematic cross-sectional view of the ring section 12g cooperating with the cover 20 and the webs 12e cooperating with the cover 20 and the guide cross member 9.

The annular section 12g is inserted in a surrounding groove 20c between the covering section 20b, the collar 20a and the outer surface 20d of the cap 20. In this case, the annular section 12g is fixedly held by the outer surface 20d of the cover 20 radially inwardly toward the floating bearing axis 5a (see fig. 2). The annular section 12g is in contact with the outer surface 20d, either directly or indirectly (e.g., via an insert or/and an adhesive). The term "radially inwardly" refers to a direction with reference to the floating bearing axis 5a (see fig. 2).

Radially outwardly, i.e. in a direction extending radially outwardly therefrom with reference to the floating bearing axis 5a, the annular section 12g is fixedly retained by a footprint section 20b of the cover 20. Here, the ring section 12g is in contact with the bottom side of the footprint section 20b, either directly or indirectly (e.g., via an insert or/and an adhesive).

the insert can be, for example, a half-split insert sleeve which completely or only partially lines the recess 20 c. The insert here can also be a coating of the recess 20c, for example a liquid seal or a sealing adhesive.

The annular section 12g is held fixedly with radial pretension in a circumferential groove 20c between the sections covering the sections 20b, the collar 20a and the outer surface 20d of the cover 20. In this case, a radial prestress FR acts radially inward (upper arrow) and a radial prestress radially outward (lower arrow) on the ring segment 12 g.

The radial pretensioning force FR can be generated, for example, in such a way that the annular section 12g is pretensioned by the circumferential compression of the cover section 20b in the circumferential groove 20c between the cover section 20b, the collar 20a and the section of the outer surface 20d of the cover 20.

By means of a corresponding radial prestress FR, the annular portion 12g of the first diaphragm air spring 12 forms a pressure-tight seal, also referred to as a pressure-tight encapsulation, in the circumferential groove 20c relative to the cover 20. The pressure-tight encapsulation forms a so-called IP protection class to prevent the penetration of pressurized liquids, for example when cleaning with high-pressure cleaners. Thus, a protection grade IP 69 according to DIN EN 60529 or a protection grade IP6K9K according to ISO20653 (6: dust-proof; 9: water-proof in high-pressure/steam jet cleaning) can be achieved.

As mentioned above, such a seal may also be realized by means of a sealing adhesive or a sealing insert as described above.

In this case, the annular section 12g is enclosed in the groove 20c of the lid 20 by a section of the outer surface 20d of the lid 20, the collar 20a of the lid 20 and the footprint section 20b of the lid 20 at an angle in the range 160 ° to 190 °, preferably 180 °. The term "wrap" is understood to mean that the outer surface of the annular section 12g is in direct or indirect contact with at least the outer surface 20d of the cover 20 and the inside of the covered section 20b of the cover 20 as described above.

When the annular portion 12g is subjected to the radial pretensioning force FR, the axial pretensioning of the annular portion 12g with the webs 12e attached thereto is also produced by the axial pretensioning force FA. In this case, the ring section 12g is supported in the groove 20c on the inner side of the collar 20a of the cover 20, wherein the web 12e is supported on the end face 9c of the guide cross member 9.

The annular section 12g has a circular cross section and can also be referred to as an O-ring section. Other cross-sectional shapes, such as square rings, may of course be used.

The groove 20c between the cover portion 20b, the collar 20a and the outer surface 20d of the cover 20 serves as a housing for the axially injection-molded annular portion 12g of the outer first diaphragm air spring 12 and at the same time controls the rolling movement caused by the wear of the brake linings 6, 6' (and the brake disk 3). In this way, the annular section 12g is compressed on both sides between the covering section 20b and the outer surface 20d of the cover 20, and the exposed position of the annular section 12g is also protected from damage.

The webs 12e, which are integrally formed on the side of the ring segment 12g facing the brake disk 3, form a support on the guide cross member 9 without play by their contact with the flat end face 9c of the guide cross member 9. This also allows the cover 20 to be securely fitted with the groove 20 c.

In addition to the structurally provided gap 25 (between the cover section 20b and the third membrane air spring section 12 c), the connection of the annular section 12g to the web 12e, which is provided with the waisted section 12f, serves for tolerance compensation between the components.

The gap 25 is provided as a structural air gap for tolerance compensation between the cover 20 with the recess 20c, the guide cross member 9 made of conventional steel and the first diaphragm air spring 12 to prevent damage.

In addition, a surrounding gap 12h is provided between the radially inner surface of the tab 12e and the outer surface 20d of the cover 20.

Fig. 4 shows a schematic plan view of a disc brake SB according to the invention in a partially sectional view in the worn state of the brake linings 6, 6'. Fig. 5 shows an enlarged schematic cross-sectional view of the floating bearing 5 according to the designation V of fig. 4 in a second position. Fig. 6 shows an enlarged schematic sectional view of the marking VI according to fig. 5.

Fig. 5 and 6 show a second position of the floating bearing 5, in which the brake linings 6, 6' (and the brake disk 3) of the disk brake SB are worn.

In the second position, i.e. in the case of worn brake linings 6, 6', the first diaphragm air spring section 12a of the first diaphragm air spring 12 is partially turned 180 ° below the outer facing portion of the diaphragm air spring 12 with the second diaphragm air spring section 12b and the third diaphragm air spring section 12 c. The connecting section 12d is bent over the cover section 20b of the cover 20 outwardly, i.e. away from the brake disk 3.

The annular section 12g is arranged continuously in a pressure-tight manner in the groove 20c of the cover 20.

In the central inner region of the connection between the inner sleeve 11 and the second diaphragm air spring 14 (also referred to as the inner diaphragm air spring 14), there is a stop ring 15 with a clip connection. In this case, the second diaphragm air spring 14 is connected on the one hand to the guide sleeve 7 and on the other hand to the guide cross member 9, wherein a stop ring 15 is provided for connection to the guide sleeve 7, which stop ring engages with a circumferential locking lug 23 as a hook-shaped undercut in a circumferential locking groove 24 of the inner sleeve 11, when the second diaphragm air spring 14 is injection-molded onto the other edge region of the stop ring 15. In this way, the two parts are connected to one another in a form-fitting manner.

The second diaphragm air spring 14 covers the free outer circumferential region of the guide cross member 9.

The stop ring 15 has on its outer surface a surrounding groove 15b between two surrounding projections 15 a. In this groove 15b a seal 22 is arranged in a protected position, which has a separate double sealing lip. The seal 22 may also be injection molded. Thus, a pressure-tight encapsulation is achieved in this regard. The double sealing lips of the seal 22 cooperate with the inner wall of the caliper bore 21, which is a bore of the inner sleeve 11(HNBR elastomer) designed as a fitting for injection molding into the metal sleeve of the outer sleeve 13 and is sealed in this way.

DE102012021690a1 describes such a radial seal 22 in detail for the purpose of sealing in the brake caliper opening 21 with an injection-molded sealing lip. In contrast, however, the recess 15b in the stop ring 15 has a separately injection-molded seal 22 with a double sealing lip.

The location facing the brake disk 3 and thus subjected to higher temperature loads is, for example, a sealing element in the form of a silicone membrane air spring as a second membrane air spring 14, which is injection-molded onto the already described stop ring 15. The other end of the inner second diaphragm air spring 14 (silicone diaphragm air spring) is sealed radially as a flange 17 in an annular groove 18 in the guide cross member 9 and is pressed on both sides and fixed in a form-fitting manner by means of a retaining ring 16. For this purpose, the retaining ring 16 has a circumferential annular section 16a which extends axially away from the brake disk 3. The second diaphragm air spring 14 is bent around this annular section 16 a.

The retaining ring 16 then fulfils the function of shielding the silicone membrane air spring as the second membrane air spring 14 from temperature and mechanical damage and of ensuring the sealing function of the flange 17 (e.g. a square ring) of the injection-moulded second membrane air spring 14 in the annular groove 18 th.

The retaining ring 16 ensures that the flange 17 (square ring) is reliably sealed off from the annular groove 18 in the guide cross member 9 in that: the retaining ring ensures, by virtue of its shape, that the flange 17 (square ring) is located in the annular groove 18 with a slight pressing force, even in the case of a rolling movement.

The shape of the retaining ring 16 is designed such that it limits the path of the second diaphragm air spring 14 on the brake carrier 1 side and thus provides a safety distance to the side facing the brake disk 3. The second diaphragm air spring 14 thus executes a guided, deflected rolling movement and is not completely exposed to a temperature-sensitive region. In DE102012021690a1, "radial seals 17 in the annular groove 18 of the guide cross member 9, which are pressed on both sides by the retaining ring 16," can be found.

In this way, the guide cross member 9 is sealed by the first and second diaphragm air springs 12, 14, including the inner sleeve 11, and may be made of conventional steel rather than stainless steel.

Fig. 6a shows an enlarged schematic cross-sectional view of another exemplary embodiment of the floating bearing 5 in an unworn state.

In contrast to the first exemplary embodiment, the annular portion 12g of the first diaphragm air spring 12 is arranged in the recess 9e of the end portion 9b of the guide cross member 9. A groove 9e is formed into the end face 9c of the end section 9 b. In this case, a circumferential cover section 9h is formed, which cover section 9h is arranged radially outside the recess 9e in the end section 9b of the guide cross member 9. The cover section 9h extends axially parallel to the floating bearing axis 5 a.

The cover 20 has a collar 20a (which does not cover the section 20b) and is not supported on the head 19 of the cap screw 10, but on a shoulder 9f of a stepped bore 9g coaxial with the bore 9 a.

The annular section 12g is inserted into the groove 9e in such a way that it directly or indirectly contacts the end wall of the groove, the inside of the covering section 9h, a section of the outer surface 20d of the cap 20 and the abutment surface 20e of the collar 20a of the cap 20.

By pressing the outer surface 20d of the cover 20 into the stepped bore 9g of the end section 9b of the guide cross member 9, the annular section 12g of the first diaphragm air spring 12 is pressed axially against the end wall of the recess 9e with an axial pretensioning force FA and is pretensioned. At the same time, a radial pretension is thereby also produced in the annular section 12g, which is radially supported on the underside of the end section 9h and on the outer surface 20d of the cover 20.

The aforementioned gap 25 is provided between the abutment surface 20e of the collar 20a of the cover 20 and the end face 9c of the end section 9b of the guide cross member 9.

The material of the cover 20 may be metal, a combination of suitable plastics and metal, or a suitable plastic.

The invention is not limited to the described embodiments but may be modified within the scope of the claims.

For example, it is conceivable to provide a sealing function on cover 20 instead of a sealing function between annular section 12g of first diaphragm air spring 12 and cover 20. In this case, the outer surface 20d of the cover 20 can be sealed with respect to the guiding beam 9 in the associated hole 9a of the guiding beam 9 by suitable sealing means. This can be achieved, for example, by an integrally formed sealing lip on the outer surface 20d of the lid 20. The cover 20 may be provided with reinforcement by means of suitable inserts in its body. This is not shown, but is easily conceivable. In addition, an opening may be provided at the bottom of the cover 20 to mount the cap screw 10.

List of reference numerals

1 brake support

2 brake caliper

2a brake application zone

2b, 2c bearing segment

3 brake disc

3a brake disc axis of rotation

4 fixed bearing

4a fixed bearing axis

5 floating bearing

5a floating bearing axis

6. 6' brake lining

7 guide sleeve

8 neck ring

9 guide beam

9a hole

9b end section

9c end face

9d head hole

9e groove

9f shoulder

9g stepped hole

10 screw with cap

11 inner sleeve

11a shoulder

12 first film type air spring

12a, 12b, 12c membrane air spring section

12d connecting section

12e tab

12f corset part

12g ring segment

12h gap

13 outer sleeve

13a, 13b ends

14 second diaphragm air spring

14a connecting section

15 stop ring

15a projection

15b groove

15c connecting section

16 retaining ring

16a ring segment

17 Flange

18 annular groove

19 head part

20 cover

20a cervical collar

20b coverage area segment

20c groove

20d outer surface

20e abutment surface

21 brake caliper hole

22 seal

23 locking lug

24 locking groove

25 gap

26. 26a gap

FA axial pre-tightening force

FB radial pretightening force

SB disc brake