Bearing coupling ring, retractor and reset mechanism, disc brake, clutch system

Abstract

The invention relates to a bearing coupling ring (10) for supporting a return shaft (120) of a disc brake, wherein the bearing coupling ring (10) extends around an annular axis (12), the bearing coupling ring (10) comprising: an annular shell side (20) facing away from the annular axis (12) and an annular inner side (22) facing the annular axis (12), a radial fixing support (26) arranged on the annular shell side (20), a first axial stop surface (28) arranged on the annular shell side (20), a first receiving surface (34) arranged on the annular inner side (22) and rotating around the annular axis (12), a second axial stop surface (42) arranged on the annular inner side (22), and several axial coupling claws (58), characterized in that the bearing coupling ring (10) further comprises: a second receiving surface (34) arranged on the annular inner side (22) and rotating around the annular axis (12). Recording area (48),wherein the second receiving surface (48) is designed spaced apart from the first receiving surface (34), the coupling claws (58) extend the second receiving surface (48) axially in sections, and the bearing coupling ring (10) is formed in one piece.

Description

[0001] The invention relates to a bearing coupling ring for supporting a return shaft of a disc brake, wherein the bearing coupling ring extends around an annular axis. The bearing coupling ring comprises an annular outer surface facing away from the annular axis and an inner surface facing the annular axis, a radial fixing support arranged on the annular outer surface, a first axial stop surface arranged on the annular outer surface, a first receiving surface arranged on the inner surface of the ring and rotating around the annular axis, a second axial stop surface arranged on the inner surface of the ring, and several axial coupling claws. The invention further relates to a return and / or reset mechanism, a disc brake, and a coupling system.

[0002] From EP 0 531 321 B1, WO 2015 / 117601 A1 and DE 102 60 597 B4, vehicle disc brakes are known which are equipped with an adjusting device to compensate for operational wear on the brake pads and the brake disc. This device successively adjusts the distance between the brake pads and the brake disc according to the increasing wear, thus maintaining this so-called clearance within a design-defined range. The adjusting device is actuated by a drive element which is rotatably arranged in the disc brake housing on an axis parallel to the axis of rotation of the brake disc. The drive element is set in rotation by the brake clamping device of the disc brake, e.g. by a rotary lever arranged in the brake housing, which amplifies the braking force. The drive element of the adjusting device is rotatably mounted on a centrally located shaft.This mechanism has wrench flats at the end furthest from the brake disc, allowing the adjusting device to be fully returned to its starting position by turning the shaft backwards. This is typically done when replacing worn brake pads with new ones.

[0003] The precision and reliability of the adjustment depend significantly on preventing any tilting of the adjusting device's components. To this end, in EP 0 531 321 B1, the shaft on which the adjusting device components are mounted is supported within the brake housing in such a way that it can perform slight pendulum movements. For this purpose, the shaft is supported in an opening of the brake housing by a gimbal bearing. The gimbal bearing consists of a bushing made of an inner steel ring, an outer steel ring, and an elastically deformable material sandwiched between them.

[0004] From DE 10 2016 105 611 B4, an adjustment device for a vehicle disc brake, a cardan rotary bearing, and a coupling ring are known. The cardan rotary bearing has a multi-part construction. The rotary bearing comprises two steel rings, a rubber or elastomer ring, and a sealing lip, wherein the rubber or elastomer ring and the sealing lip are bonded to the steel rings by vulcanization. A disadvantage is the multi-step manufacturing process of the rotary bearing and, in particular, its axial flexibility, which affects the precision of adjustment. Another disadvantage is the short and flexible design of the cardan rotary bearing relative to the shaft, which is achieved exclusively via four separate sliding surfaces. The longitudinal section of the steel ring adjoining the jaws is spaced apart from the shaft or, immediately after the non-free jaw ends, retracts radially outwards with a circumferential radius.The resulting space between the steel ring and the shaft is filled with flexible sealing material, does not constitute a receiving surface and serves only for sealing.

[0005] The invention is based on the objective of providing a bearing coupling ring that is easy and quick to manufacture and has a longer lifespan.

[0006] The problem underlying the invention is solved by a bearing coupling ring with the features of claim 1. The bearing coupling ring is characterized in that it further comprises a second receiving surface arranged on the inner side of the ring and circumferentially around the ring axis, wherein the second receiving surface is spaced apart from the first receiving surface. Furthermore, the coupling claws extend the second receiving surface axially in sections, i.e., parallel to the ring axis. In addition, the bearing coupling ring is formed in one piece and / or monolithically.

[0007] The one-piece design enables simple and rapid manufacturing. The number of process steps is reduced. Due to the second mounting surface circumferentially around the ring axis, a larger contact area is provided for the bearing of the return shaft, and the bearing coupling ring exhibits greater stability and / or rigidity. This counteracts the spreading of the coupling jaws, which has a positive effect on the accuracy of the clearance adjustment.

[0008] A central recess in the bearing coupling ring extends along the ring axis between a brake side facing the brake disc in the assembled state and a tool side facing away from the brake disc in the assembled state.

[0009] Preferably, the radial fixing support and / or the first axial stop surface and / or the second axial stop surface are designed to extend around the ring axis. For the purposes of the invention, "extending around the ring axis" means that the respective element or surface extends completely through 360° around the ring axis and is formed as a single, continuous piece.

[0010] Preferably, the outer surface of the ring and / or the inner surface of the ring has a substantially cylindrical contour. One or more steps may be provided in the contour.

[0011] The first receiving surface and / or the second receiving surface are preferably rigid, in particular designed to be storable.

[0012] The radial fixing support preferably extends parallel to the ring axis. The first axial stop surface and / or the second axial stop surface preferably extend perpendicular to the ring axis.

[0013] The components of the bearing coupling ring, such as the radial fixing support, the first axial stop surface, the second axial stop surface, the first receiving surface and / or the second receiving surface, are preferably integrally formed on the bearing coupling ring.

[0014] An advantageous aspect of the invention provides that the bearing coupling ring is designed as a turned part or as a sintered part. The bearing coupling ring is preferably designed with rotational symmetry, at least in sections, particularly the radial fixing support, the first axial stop surface, the second axial stop surface, the first receiving surface, and / or the second receiving surface. This further simplifies manufacturability. Due to their separate design extending around the ring axis, the coupling claws are not arranged circumferentially but individually.

[0015] An advantageous aspect of the invention provides that the bearing coupling ring is made of and / or consists of metal, in particular aluminum or an aluminum-like or aluminum-containing material. This ensures a particularly stable and lightweight bearing and coupling.

[0016] An advantageous aspect of the invention provides that the first receiving surface has a first receiving diameter and the second receiving surface has a second receiving diameter, wherein the second receiving diameter is larger than the first receiving diameter. Accordingly, the second receiving surface can come into contact with the return shaft. By spaced radially from the first receiving surface, the inclusion of a sealing element, in particular a radial shaft seal, between the second receiving surface and the return shaft is made possible.

[0017] An advantageous aspect of the invention provides that, with respect to the ring axis, the first receiving surface is axially connected to the second receiving surface, and / or that, with respect to the ring axis, the first receiving surface and the second receiving surface are arranged radially spaced apart from each other. Due to the axial proximity between the receiving surfaces, a particularly flat and compact bearing coupling ring can be provided.

[0018] An advantageous aspect of the invention provides that the bearing coupling ring has a connecting section, in particular one extending perpendicular to the ring axis and with a section width parallel to the ring axis, connecting the first receiving surface and the second receiving surface and / or the fixing section. Accordingly, the inner receiving surfaces and / or one of the receiving surfaces and the fixing support are directly connected to one another, resulting in higher relative accuracy in the adjustment process. This counteracts axial displacement between the inner receiving surfaces and the outer fixing support.

[0019] An advantageous aspect of the invention provides that the coupling claws have a claw width extending perpendicular to the ring axis, and that the section width of the connecting section is greater than the claw width. This ensures a particularly stable and rigid connection between the first and second receiving surfaces, while also providing a material-saving design in the area of ​​the coupling claws. Consequently, a stable and lightweight bearing coupling ring is provided.

[0020] An advantageous aspect of the invention provides that the connecting section has a tapered section and / or a web section, particularly one adjoining the tapered section. The section width in the tapered section preferably decreases radially outwards with respect to the ring axis. The section width in the web section is preferably constant. This ensures a stable and material-saving connection of the coupling claws to the ring shell.

[0021] An advantageous aspect of the invention provides that the first axial stop surface connects to the radial fixing support, and / or that the second axial stop surface connects to the first receiving surface and / or the second receiving surface. The second axial stop surface is preferably arranged between the first receiving surface and the second receiving surface.

[0022] An advantageous aspect of the invention provides that the first receiving surface has a first receiving length parallel to the ring axis and the second receiving surface has a second receiving length parallel to the ring axis, wherein the ratio between the first receiving length and the second receiving length is in a range between 4:1 and 1:1, in particular between 3.5:1 and 1.5:1, preferably between 3:1 and 2:1.

[0023] It is advantageous if the bearing coupling ring has a sealing element, in particular a radial shaft seal with a sealing lip. The sealing element, in particular the radial shaft seal, is preferably arranged on the first receiving surface and the second axial stop surface. Preferably, the sealing element, in particular the radial shaft seal, is designed separately from the first receiving surface and the second axial stop surface.

[0024] The problem underlying the invention is also solved by a follower and / or retractor with the features of claim 11. The invention is directed to a follower and / or retractor of a disc brake with a previously described bearing coupling ring.

[0025] An advantageous aspect of the invention provides that the follow-up and / or resetting device has a resetting shaft, wherein the resetting shaft is supported on the coupling jaws, in particular their inner surface, and on the second receiving section, in particular on the second receiving surface. This provides a larger bearing area.

[0026] An advantageous aspect of the invention provides that the retractor and / or resetter has a radial shaft seal with a sealing lip. The radial shaft seal preferably bears against the first receiving surface and against the second axial stop surface. The sealing lip is preferably arranged circumferentially on the resetter shaft with respect to the ring axis.

[0027] It is advantageous if the radial shaft seal is supported against an annular washer, which in turn is secured by a retaining ring arranged in a groove on the outer circumference of the return shaft. For the purpose of a circumferential boundary surface, an annular washer can be located between the radial shaft seal and the retaining ring.

[0028] The problem underlying the invention is also solved by a disc brake with the features of claim 14. The invention relates to a disc brake with a previously described follow-up and / or return mechanism or a previously described bearing coupling ring.

[0029] An advantageous aspect of the invention provides that the disc brake has a brake caliper housing, and wherein the bearing coupling ring is supported radially outside the brake caliper housing with respect to the ring axis, in particular exclusively, axially frictionally via the fixing support and / or axially positively via the first axial stop surface.

[0030] The brake caliper housing preferably has an opening through which the adjuster can be inserted. The opening is preferably closable by means of a cap, which is preferably connected to the housing by means of a threaded connection. The cap preferably secures a further sealing element, in particular an O-ring, in a chamfer of the opening, thus sealing the cap and the housing.

[0031] The problem underlying the invention is also solved by a coupling system with the features of claim 16. The coupling system comprises a previously described bearing coupling ring and a counter coupling ring. The counter coupling ring preferably has counter claws which interact with the coupling claws of the bearing coupling ring to form an axially movable and rotationally fixed connection. The bearing coupling ring preferably has a second receiving section, wherein the second receiving surface is formed by the second receiving section.

[0032] Further advantages, features, and details will become apparent from the following description, in which various embodiments of the invention are illustrated with reference to the drawing. The features mentioned in the claims and the description can each be essential to the invention individually or in any combination.

[0033] They show: Fig. 1 A view of a vehicle disc brake perpendicular to the brake clamping axis; Fig. 2 a longitudinal section through the vehicle disc brake equipped with an adjusting device along the brake clamping axis according to Fig. 1; Fig. 3 a detailed view of the longitudinal section of the bearing coupling ring of the adjusting device according to Fig. 2; Fig. 4 an exploded view of the coupling system of the adjusting device according to Fig. 2; Fig. 5 an exploded view of the individual parts of the adjusting device according to Fig. 2; and Fig. 6A-B second further views of the bearing coupling ring of the coupling system according to Fig. 4.

[0034] Fig. 1 and Fig. Figure 2 shows an overview of a pneumatically actuated disc brake 79 with an integrated device for adjusting the wear-related air clearance of the disc brake 79. Such a device is used, for example, in a sliding caliper disc brake intended for commercial vehicles to compensate for the brake pad wear associated with driving operation, but also for the wear on the brake disc 82.

[0035] The adjusting device, together with elements of the brake tensioning, is arranged in a brake housing 80, which can in particular be the brake caliper of the disc brake.

[0036] The disc brake also includes the component in Fig. Figure 2 shows a section of a brake disc 82 connected to the vehicle wheel, against which a brake pad 84 can come into contact on each of its two sides. The brake pad 84 has, in the usual manner, a backing plate 86 and the actual friction lining 88.

[0037] The inner brake pad 84 is directly acted upon with brake pressure by a pressure piston 90 which is movable relative to this inner brake pad 84 and which, when the brake is applied, bears against the backing plate 86 of this inner brake pad 84. The pressure piston 90 is connected in a threaded connection 92 suitable for transmitting the full braking forces to a pressure piece 94, which is arranged to be longitudinally movable in the brake housing 80.

[0038] A clamping lever 96 is supported against the pressure piece 94. The clamping lever 96 is mounted in the brake housing 80 on a pivot axis parallel to the braking surfaces of the brake disc 82, and it is provided with a lever arm 98 facing away from the pressure piece 94. The force element of the vehicle brake acts against the lever arm 98. In a pneumatically actuated disc brake, this force element is a pneumatic cylinder, preferably a diaphragm cylinder. The force generated by the force element is converted via the lever arm 98 into a pivoting of the clamping lever 96, which, due to the leverage, results in a pressure on the pressure piece 94 that amplifies the force of the force element. The arrangement consisting of the force element, the lever arrangement, and the pressure piece 94 forms the clamping device of the vehicle brake.

[0039] The clamping lever 96 acts as an eccentric to increase pressure. The fork-shaped design of the clamping lever 96 shown is preferred. In this design, the actuating force, and thus the braking force, is transmitted equally to both sides of the adjusting device centrally located on axis A and onto the pressure piece 94.

[0040] In the unbraked position, a gap (clearance) exists between the brake disc 82 and each of the two brake pads 84 to prevent the parts from rubbing against each other. The adjusting device compensates for this clearance, which increases over time due to wear on the pads and the brake disc 82. For a simple and compact brake design, this adjusting device is at least partially integrated into the pressure piston 90, which is centrally located in the brake housing 80. For this purpose, the pressure piston 90 has a cavity 100 that is open on the side facing away from the brake disc. On the side facing the brake disc 82, however, the pressure piston 90 is closed.

[0041] The adjusting device includes a drive element 102, which is rotatably arranged within the brake housing 80 of the disc brake 79 on an axis A parallel to the axis of rotation of the brake disc 82. During the braking process, the drive element 102 can be rotated about the axis A by the clamping device of the disc brake 79, and in particular by the action of the clamping lever 96.

[0042] The adjusting device also includes an adjusting element 104 arranged on the same axis A, and a transmission device between the drive element 102 and the adjusting element 104. The transmission device allows the adjusting element 104 to be successively moved into rotational movements in the same direction by the drive element 102. A coil spring 106, also arranged on axis A, serves as the transmission device.

[0043] The adjusting element 104 is rotationally fixed relative to the surrounding pressure piston 90, but axially movable. For this purpose, the pressure piston 90 is provided on its inner side with longitudinal grooves 108 in which projections or lugs 110 formed on the outside of the adjusting element 104 are longitudinally guided. This achieves non-rotatable longitudinal guidance of the adjusting element 104 relative to the pressure piston 90. The relatively short longitudinal lugs 110 compensate for a slight pivoting movement that is unavoidable during brake clamping.

[0044] The drive element 102 is essentially stationary in the longitudinal direction of axis A, with respect to the brake housing 80. The drive element 102 is provided with an outwardly projecting arm 114. The arm 114 forms a cam 112 ( Fig. 2), into which a pin 116 arranged on the clamping lever 96 engages. The cam 112 on the arm 114 and the pin 116 together form a gear mechanism through which the drive element 102 can be driven by the movement of the clamping lever 96. Pivoting the clamping lever 96 thus causes the drive element 102 to rotate about axis A. In this process, the axial drive movement is converted into a rotary movement. This involves not only forces in the direction of rotation, but also unwanted axial forces that are introduced into the adjusting unit. These forces must be securely supported without causing the adjusting components to shift axially.

[0045] For an overall axial design of the adjusting device, both the drive element 102 and the adjusting element 104 are located on a reset shaft 120 arranged centrally on the axis A. The reset shaft 120 is rotatable, but axially immovable with respect to the brake housing 80, whereby the aforementioned axial forces are reliably supported or transferred into the brake housing 80.

[0046] The adjusting element 104 is fixedly connected to the reset shaft 120, and in particular is rotationally fixed. The drive element 102, on the other hand, is rotatably mounted on the reset shaft 120.

[0047] At its end furthest from the brake disc 82, the reset shaft 120 is provided with a polygonal flat 118 serving as a wrench flat. A tool can be attached to this flat to fully return the pressure piston 90 to its initial position by rotating the reset shaft 120. This is typically done when replacing worn brake pads 84 with new ones. Before replacing old brake pads 84 with new ones, the pressure piston 90 must be manually returned to its initial position. For this purpose, the reset shaft 120, and thus also the adjusting element 104 and the pressure piston 90, is rotated in a direction opposite to the direction of rotation that occurs successively during the adjustment process.

[0048] The rotational movement during resetting is not transferred to the drive element 102, since a helical section of the coil spring 106 shrinks in this case, and this helical section slips through the adjusting element 104 in the manner of a freewheel.

[0049] The coiling spring 106, which serves to transmit rotation between the drive element 102 and the adjusting element 104, can combine the functions of a one-way coupling with the function of an overload coupling. Details of the coiling spring 106 and its function are described in patent application WO 2015 / 117601 A1.

[0050] The return shaft 120 is supported in two ways relative to the brake housing 80, each support being indirect. The first support is provided by the adjusting element 104, which is guided in the pressure piston 90. The pressure piston 90, in turn, is supported via the threaded connection 92 in the pressure piece 94, which is guided opposite the brake caliper. The second support is provided at the other end, i.e., the end facing away from the brake disc. There, the return shaft 120 is indirectly supported via a bearing coupling ring 10 in a round opening 80A of the brake housing 80.

[0051] The bearing coupling ring 10 extends according to Fig. 4 along an annular axis 12, which, in the assembled state, runs coaxially to axis A. The bearing coupling ring 10 is formed in one piece as a turned or sintered part and is made of a metal, in particular aluminum or brass. Preferably, the bearing coupling ring 10 consists exclusively of aluminum, with the exception of an arranged sealing agent. The bearing coupling ring 10 has a brake side 14 facing the brake disc 82 in the assembled state and a tool side 16 facing away from the brake disc 82. The bearing coupling ring 10 has a central recess 18, which extends along the annular axis 12 between the brake side 14 and the tool side 16. Accordingly, the bearing coupling ring 10 has an annular shell side 20 and an annular inner side 22, wherein the annular inner side 22 adjoins the recess 18 and faces the annular axis 12, and the annular shell side 20 faces away from the annular axis 12.

[0052] The bearing coupling ring 10 has according to Fig. 3 and Fig. 4 on the ring mantle side 20 a fixing section 24 with a radial fixing support 26 and with a first axial stop surface 28. The bearing coupling ring 10 is supported radially outside the brake housing 80 with respect to the ring axis 12, in particular exclusively, axially frictionally via the radial fixing support 26 and / or axially positively via the first axial stop surface 28.

[0053] The fixing section 24 is according to Fig. 3 is set back radially inwards relative to a base section 30 of the bearing coupling ring 10 with respect to the ring axis 12. The radial fixing support 26 is arranged at the radially outer end of the fixing section 24. The radial fixing support 26 extends parallel to the ring axis 12. In addition, the base section 30 projects axially relative to the fixing section 24 on the brake side 14. The first axial stop surface 28 is arranged on a side of the base section 30 that is perpendicular to the radial fixing support 26. The first axial stop surface 28 extends perpendicular to the ring axis 12 and faces the tool side 16.

[0054] The fixing section 24 is connected according to Fig. 3 radially inside a first receiving section 32 with a first receiving surface 34. The fixing section 24 base section 30 is preferably arranged between the first receiving section 32 and the base section 30. The first receiving surface 34 faces the ring axis 12 and extends completely around the ring axis 12. The first receiving section 32 projects axially from the fixing section 24 on the tool side 16. The first receiving surface 34 runs parallel to the ring axis 12.

[0055] The axial width of the base section 30 is preferably smaller than the axial width of the fixer section 24 and / or the axial width of the first receiving section 32.

[0056] The first recording section 32 is followed according to Fig. 3 radially inside, a connecting section 36 with a tapered section 38 and a web section 40 is attached. Thus, the first receiving surface 34 and the second receiving surface 48 are directly connected to each other, resulting in high relative accuracy with regard to adjustment. This prevents axial displacement between the fixing section 24 and the tapered section 38, from which coupling claws 58 extend. The connecting section 36 has a second axial stop surface 42, which faces the tool side 16 and is perpendicular to the ring axis 12. The connecting section 36 connects the first receiving section 32 and a second receiving section 44. The tapered section 38 connects to the second receiving section 44. The web section 40 connects to the first receiving section 32.The connecting section 36 has a section width 46 running parallel to the ring axis 12, which tapers in the tapered section 38 from the second receiving section 44 towards the web section 40. The section width 46 is constant in the web section 40.

[0057] The second recording section 44 proceeds according to Fig. 4 completely around the ring axis 12. The second receiving section 44 is ring-shaped. The second receiving section 44 has a second receiving surface 48 facing the ring axis 12. In the assembled state, the second receiving surface 48 is supported by the return shaft 120. Thus, in addition to the inner surfaces 68 of the partial coupling jaws 58, a large contact surface, enclosed around the return shaft 120, is provided for the bearing of the return shaft 120. The axial receiving length 52 of the second receiving surface 48 is between 1:2 and 1:5, preferably between 1:3 and 1:4, of the axial length of the coupling jaws 65. Furthermore, the bearing coupling ring 10 exhibits overall higher stability and / or stiffness. This has a positive effect on the accuracy of the clearance adjustment.

[0058] The first recording surface 34 shows according to Fig. 3 a first recording length 50 running parallel to the ring axis 12 and the second recording surface 48 a second recording length 52 running parallel to the ring axis 12, wherein a ratio between the first recording length 50 and the second recording length 52 is in the range between 4:1 and 1:1, in particular 3:1 and 2:1.

[0059] The first recording surface 34 and the second recording surface 48 are according to Fig. The 3 surfaces are radially spaced apart from each other with respect to the ring axis 12 and are axially adjacent to each other. The first receiving surface 34 has a first receiving diameter 54 and the second receiving surface 48 has a second receiving diameter 56, wherein the first receiving diameter 54 is larger than the second receiving diameter 56.

[0060] All previously described elements of the bearing coupling ring 10 are preferably designed to be rotationally symmetrical.

[0061] The second recording section 44 is connected according to Fig. 4 and Fig. 5. Several, in particular four, coupling claws 58 are attached. The coupling claws 58 extend parallel to the ring axis 12 and project axially from the second receiving section 44. The coupling claws 58 are flush with the second receiving surface 48 on the inner surface 22 of the ring. Thus, the coupling claws 58 axially extend the second receiving surface 48 section by section. A large contact area is therefore provided for the return shaft 120 by the second receiving surface 48 and the coupling claws 58, resulting in good sliding properties with low wear. The second receiving section 44 prevents the coupling claws 58 from spreading apart.

[0062] The coupling claws 58 have according to Fig. 3 on one of the claw inner sides 68 facing the ring axis 12 a cylindrical inner contour is formed, so that a flat support on the reset shaft 120 is also achieved here.

[0063] Two adjacent coupling claws 58 are according to Fig. The 4 surfaces are each separated by a gap. In the area of ​​a gap, the second receiving surface 48 is not extended axially.

[0064] The coupling claws 58 have according to Fig. 3 each have a claw width 66 extending perpendicular to the ring axis 12, wherein the section width 46 of the connecting section 36 is larger than the claw width 66 of the coupling claws 58. All coupling claws 58 preferably have the same claw width 66.

[0065] The coupling claws 58 and the gaps provided between them form positive locking elements, through which a rotationally fixed connection of the bearing coupling ring 10 with a separate counter coupling ring 74 is achieved according to Fig. 4. For this purpose, the counter-coupling ring 74 is provided at its ring opening 60 with corresponding positive locking elements, namely with first circumferential sections 62 projecting alternately towards the axis A or ring axis of the bearing coupling ring 10 and second circumferential sections 64 projecting back towards the axis A or ring axis, which alternate with each other. This achieves a pure rotary coupling, which thus allows free longitudinal movement of the counter-coupling ring 74 relative to the bearing coupling ring 10. In the assembled state, the counter-coupling ring 74, in particular the first circumferential sections 62, is oriented towards the second receiving section 44 against a Fig. 3 wave springs 76 not shown, movable.

[0066] Furthermore, according to Fig. 3. A radial shaft seal 70 with a sealing lip 72 is arranged on the second axial stop surface 42, the second receiving surface 48, and the return shaft 120. The radial shaft seal 70 is supported on the first receiving surface 34 and against the second axial stop surface 42. The sealing lip 72 is preferably arranged circumferentially on the return shaft 120 with respect to the ring axis 12. The radial shaft seal 70 is a replaceable standard component and is therefore easy to maintain. In addition, the radial shaft seal is axially accessible from the tool side 16 through the radial distance between the first receiving surface 34 and the second receiving surface 48.

[0067] A spring element 78, which is designed as a wave spring 76, is supported according to Fig. 2 and Fig. 5 on the one hand against the bearing coupling ring 10, in particular the connecting section 36 and / or second receiving section 44, and on the other hand against the counter coupling ring 74, which for this purpose is provided with a circumferential step that partially receives the wave spring 76 and centers it with respect to the axis A. For further explanation of the spring element 78, its arrangement between the bearing coupling ring 10 and the counter coupling ring 74, and the toothed coupling structures of the counter coupling ring 74 and a collar arranged on the return shaft 120, reference is made to paragraphs

[0046] to

[0055] as well as Fig. 4 and Fig. 5 of DE 10 2016 105 611 referenced.

[0068] For axial fixing of the reset shaft 120 to the bearing coupling ring 10, the fixing section 24 and / or the first receiving section 32 is supported against a ring disc, which in turn is secured by a retaining ring, which sits in a groove on the outer circumference of the reset shaft 120.

[0069] A cap 122 made of a soft plastic can be placed on the outside of the housing opening 80A to further seal it. The cap 122 also helps to prevent the ingress of moisture and dust into the area of ​​the rotary bearing and the adjustment mechanism. The cap 122 preferably has an external thread that is screwed into a corresponding internal thread in the housing opening 80A. The screwed-in cap 122 secures a further sealing element, in particular an O-ring 124, preferably made of a flexible material, in a housing chamfer 126 of the housing opening 80A, thereby ensuring a reliable seal between the brake housing 80 and the cap 122. The housing chamfer 126 is preferably arranged circumferentially around the axis A. Reference symbol list 10 bearing coupling ring 12 Ring axle 14 Brake side 16 Tool page 18 Exclusion 20 Ring mantle side 22 inner ring 24 Fixing section 26 radial fixing support 28 first axial stop surface 30 Basic section 32 first recording section 34 first recording area 36 Connecting section 38 Rejuvenation section 40 Bridge section 42 second axial stop surface 44 second recording section 46 section width 48 second recording area 50 first recording length 52 second recording length 54 first recording diameter 56 second recording diameter 58 Clutch claw 60 ring opening 62 first section 64 second section 66 claw width 68 Inside of the claw 70 Radial shaft seal 72 Sealing lip 74 Counter-coupling ring 76 wave spring 78 Spring element 79 disc brake 80 brake housings 80A opening 82 Brake disc 84 brake pads 86 Backing plate 88 friction lining 90 printing stamps 92 Threaded connection 94 printed piece 96 tensioning levers 98 Lever arm 100 cavity 102 Drive element 104 Adjusting element 106 coiling spring 108 longitudinal grooves 110 noses 112 Scenery 114 Arm 116 cones 118 Polygonal 120 reset shaft 122 cap 124 O-ring 126 Housing chamfer QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] EP 0 531 321 B1 [0002, 0003] WO 2015 / 117601 A1 [0002, 0049] DE 102 60 597 B4

[0002] DE 10 2016 105 611 B4

[0004] DE 10 2016 105 611

[0067]

Claims

[1] Bearing coupling ring (10) for bearing a return shaft (120) of a disc brake (79), wherein the bearing coupling ring (10) extends about a ring axis (12), the bearing coupling ring (10) comprising: - one side of the ring mantle (20) facing away from the ring axis (12) and one inner side of the ring (22) facing the ring axis (12), - a radial fixing support (26) arranged on the ring mantle side (20), - a first axial stop surface (28) arranged on the ring mantle side (20), - a first receiving surface (34) arranged on the inner side (22) of the ring and circumferential around the ring axis (12), - a second axial stop surface (42) arranged on the inner side (22) of the ring, and - several axial coupling claws (58), characterized by , that the bearing coupling ring (10) further comprises: - a second receiving surface (48) arranged on the inner side (22) of the ring and circumferential around the ring axis (12), wherein the second receiving surface (48) is spaced apart from the first receiving surface (34), that the coupling claws (58) extend the second receiving surface (48) axially in sections, and that the bearing coupling ring (10) is formed in one piece. [2] Bearing coupling ring (10) according to claim 1, wherein the bearing coupling ring (10) is designed as a turned part or as a sintered part. [3] Bearing coupling ring (10) according to claim 1 or 2, wherein the bearing coupling ring (10) is made of and / or consists of metal, in particular aluminium. [4] Bearing coupling ring (10) according to one of the preceding claims, wherein the first receiving surface (34) has a first receiving diameter (54) and the second receiving surface (48) has a second receiving diameter (56), and wherein the second receiving diameter (56) is larger than the first receiving diameter (54). [5] Bearing coupling ring (10) according to one of the preceding claims, wherein with respect to the ring axis (12) the first receiving surface (34) is axially connected to the second receiving surface (48), and / or wherein with respect to the ring axis (12) the first receiving surface (34) and the second receiving surface (48) are arranged radially spaced apart from each other. [6] Bearing coupling ring (10) according to one of the preceding claims, wherein the bearing coupling ring (10) has a connecting section (36) connecting the first receiving surface (34) and the second receiving surface (48) and / or the fixing support (26) with a section width (46) extending parallel to the ring axis (12). [7] Bearing coupling ring (10) according to claim 6, wherein the coupling claws (58) have a claw width (66) extending perpendicular to the ring axis (12), and wherein the section width (46) is greater than the claw width (66). [8] Bearing coupling ring (10) according to claim 6 or 7, wherein the section width (46) of the connecting section (36) has a tapered section (38) and / or a web section (40) with respect to the ring axis (12), and wherein the section width (46) decreases radially outwards in the tapered section (38) and / or is constant in the web section (40). [9] Bearing coupling ring (10) according to one of the preceding claims, wherein the first axial stop surface (28) connects to the radial fixing support (26), and / or wherein the second axial stop surface (42) connects to the first receiving surface (34) and / or the second receiving surface (48). [10] Bearing coupling ring (10) according to one of the preceding claims, wherein the first receiving surface (34) has a first receiving length (50) extending parallel to the ring axis (12) and the second receiving surface (48) has a second receiving length (52) extending parallel to the ring axis (12), wherein the ratio between the first receiving length (50) and the second receiving length (52) is in a range between 4:1 and 1:1, in particular between 3:1 and 2:

1. [11] Adjusting and / or resetting a disc brake (79) with a bearing coupling ring (10) according to one of the preceding claims. [12] Resetting and / or resetting device according to claim 11, wherein the resetting and / or resetting device has a resetting shaft (120), and wherein the resetting shaft (120) is supported on the jaw couplings and on the second receiving surface (48). [13] Resetting and / or resetting device according to claim 12, wherein the resetting and / or resetting device has a radial shaft seal (70) with a sealing lip (72), and wherein the radial shaft seal (70) is supported on the first receiving surface (34) and opposite the second axial stop surface (42), and / or wherein the sealing lip (72) is arranged circumferentially on the resetting shaft (120) with respect to the ring axis (12). [14] Disc brake with a follow-up and / or return mechanism according to one of claims 11 to 13 or a bearing coupling ring (10) according to one of claims 1 to 10. [15] Disc brake (79) according to claim 14, wherein the disc brake (79) has a brake caliper housing (80), and wherein the bearing coupling ring (10) is supported radially outside the brake caliper housing (80) with respect to the ring axis (12), in particular exclusively, via the fixing support (26) axially frictionally and / or via the first axial stop surface (28). [16] Coupling system comprising a bearing coupling ring (10) according to any one of claims 1 to 10 and a counter coupling ring (74) cooperating with the bearing coupling ring (10).