BRAKE ASSEMBLY WITH A TOOTHED PART AND AT LEAST ONE SPRING PART

Description

[0001] The invention relates to a brake arrangement with a toothed part having teeth and at least one spring part.

[0002] It is generally known that a brake assembly is designed with a toothed part having teeth, such as an internally toothed brake pad carrier.

[0003] From the US 2006 / 0 027 428 A1 A brake arrangement is known.

[0004] From the DE 34 41 304 A1 A disc brake system is known.

[0005] From the DE 198 55 025 A1 The most recent state of the art is a suspension for a gear coupling.

[0006] From the DE 10 2006 019 453 A1 A gear coupling with suspension and electric motor with brake is known, which is connected via a gear coupling.

[0007] The invention is therefore based on the objective of operating a braking system safely.

[0008] According to the invention, the problem is solved in the brake arrangement according to the features specified in claim 1.

[0009] Important features of the invention in the brake arrangement with a toothed part having teeth and at least one spring part are that the spring part has a yoke area which is connected to a first bracket area of ​​the spring part which is connected at its end facing away from the yoke area to a first end area of ​​the spring part, wherein the spring part is mounted onto the teeth in such a way that the first bracket area of ​​the spring part is at least partially arranged in a tooth gap of the toothing, the yoke area engages in a first annular groove formed on the toothed part, the first end area engages in a second annular groove formed on the toothed part.

[0010] An advantage of this design is that the spring element elastically grips the toothed section and is positively connected in the radial direction, as the end and yoke sections engage in their respective annular grooves. Circumferentially, the spring element is positively locked by the toothing. An axially positive connection is achieved because the annular grooves are arranged radially spaced from the toothing. The holding force, however, is generated elastically by the axial expansion of the spring element. The spring element allows a force to be exerted on another toothed section by elastic bending of the spring element, with the teeth of the second toothed section engaging with those of the first. The force is essentially radially directed. This reduces rattling, i.e., noise emissions from the brake assembly.Furthermore, the spring component ensures well-defined operation, as there is no play between the brake pad carrier and the drive pin. This also contributes to safe and precise operation.

[0011] In an advantageous embodiment, a second bracket area of ​​the spring part, spaced apart from the first bracket area, is connected to the yoke part, which at its end facing away from the yoke part is connected to a second end area of ​​the spring part. the second bracket area of ​​the spring part is at least partially arranged in a second tooth gap of the toothing, the second end area engages in the second annular groove formed on the toothed part.

[0012] An advantage of this design is that the spring element is held symmetrically and thus centered. This allows for symmetrical support of the spring element, generating a radially oriented compressive force that is transferred to the subsequent toothed section. The well-defined, secure fit of the spring element also ensures a well-defined, centered position of the brake pad carrier, thus centering it towards the drive pin. In a further development, several identical spring elements are arranged around the circumference of the toothed section, spaced regularly and / or uniformly from one another in the circumferential direction.

[0013] In an advantageous embodiment, the first annular groove is incorporated into a flat surface area of ​​the toothed part, the normal vector of which is aligned parallel to the axial direction. wherein the ring axis of the second annular groove coincides with the axis of rotation of the toothed part, in particular wherein the groove opening of the first annular groove is open towards the axial direction, and in particular wherein the annular groove is continuous in the circumferential direction around the axis of rotation. It is advantageous that the first flat surface area is an end face oriented towards the axial direction. Thus, the yoke area engages in the first annular groove from the axial direction. Therefore, a positive-locking connection of the spring part with the toothed part in the radial direction can be easily achieved.

[0014] In an advantageous embodiment, the second annular groove is incorporated into a second flat surface area of ​​the toothed part, the normal vector of which is aligned parallel to the axial direction. wherein the annular axis of the first annular groove coincides with the axis of rotation of the toothed part, and in particular wherein the groove opening of the second annular groove is open in the opposite direction to the axial direction. It is advantageous that the second flat surface area is an end face oriented in the axial direction. Thus, the end regions engage in the second annular grooves, which are open in the opposite direction to the axial direction. Therefore, a positive-locking connection in the radial direction between the spring part and the toothed part can be achieved in a simple manner.

[0015] In an advantageous embodiment, the toothing is external, and the radial spacing area covered by the first and second annular grooves, relative to the axis of rotation of the toothed part, is spaced apart from the radial spacing area covered by the toothing and / or radially within the radial spacing area covered by the toothing, particularly wherein the toothed part is designed as a driver. It is advantageous that the spring element can be attached to the toothing from the radial outside, clamping its yoke region or end regions into the annular grooves. Thus, the spring element, which expands when attached to the toothing, can be easily fastened to the toothed part.

[0016] In an alternative advantageous embodiment, the toothing is internal, and the radial spacing area covered by the first and second annular grooves, relative to the axis of rotation of the toothed part, is spaced apart from the radial spacing area covered by the toothing and / or radially outside the radial spacing area covered by the toothing, particularly wherein the toothed part is designed as a brake pad carrier. It is advantageous that the spring part can be slipped onto the toothing from the radial inside, clamping its yoke area or end areas into the annular grooves. Thus, the spring part, which expands when slipped onto the toothing, can be easily fastened to the toothed part.

[0017] In an advantageous embodiment, the brake arrangement has a shaft, in particular a rotor shaft of an electric motor, A drive lug is mounted on the shaft and non-rotatably connected to it, and a brake pad carrier is mounted on the drive lug. An internal toothing of the brake pad carrier engages with an external toothing of the drive lug, so that the brake pad carrier is non-rotatably connected to the drive lug but is axially displaceable relative to it. An advantage of this design is that the brake can be electromagnetically actuated. Furthermore, the brake pad carrier is axially displaceable on the drive lug and can thus be pressed against a braking surface, in particular an armature disc.

[0018] In an advantageous embodiment, the brake arrangement has a magnetic body, in particular a ferromagnetic magnetic body, in which a currentable coil, in particular a coil winding, is received. wherein the shaft is rotatably mounted by means of a bearing received in a housing part, in particular a bearing flange, in particular relative to the magnet body, wherein a ferromagnetic armature disk is arranged axially between the brake pad carrier and the magnet body, wherein the armature disk is rotationally fixed to the magnet body but is arranged to be axially displaceable, in particular relative to the magnet body, wherein when the coil is energized the armature disk is pulled towards the magnet body against the spring force generated by spring elements supported on the magnet body and when the coil is not energized the armature disk is pressed onto the brake pad carrier by the spring elements in such a way that the brake pad carrier is pressed onto a braking surface arranged on the side of the brake pad carrier facing away from the armature disk, in particular wherein the braking surface is formed either on a bearing flange of the electric motor,wherein a bearing rotatably supporting the rotor shaft is received in the bearing flange and the bearing flange is non-rotatably connected to the magnet body, or is formed on a sheet metal part non-rotatably connected to the magnet body.

[0019] A key advantage is that the brake engages automatically in the event of a power failure, thus increasing safety. Furthermore, the spring mechanism ensures precise operation, eliminating any play between the brake pad carrier and the drive pin. This also contributes to safe and reliable operation.

[0020] In an advantageous embodiment, the first bracket section, supported on the first annular groove, is elastically deflected such that it presses against a first tooth tip of the teeth of a second toothed section, particularly in a radial direction, with the teeth of the second toothed section being in mesh with the teeth of the first toothed section. It is advantageous that the second toothed section is centered and aligned with the first toothed section. This ensures well-defined, backlash-free, and therefore reliable operation.

[0021] In an advantageous embodiment, the second bracket section, supported on the second annular groove, is elastically deflected such that it presses against a second tooth tip of the teeth of a second toothed part, particularly in a radial direction, with the teeth of the second toothed part being in mesh with the teeth of the first toothed part. This is advantageous because it enables a backlash-free and thus well-defined fit of the second toothed part relative to the first toothed part, thereby ensuring reliable operation.

[0022] In an advantageous embodiment, the spring part is manufactured as a bent part made of round wire.

[0023] The advantage here is that production is cost-effective and bending can be carried out with high precision, so that identical spring parts can be produced that can be arranged at regular intervals around the circumference of the toothed part.

[0024] In an advantageous embodiment, the two end regions of the spring element are spaced apart circumferentially and / or arranged at the same second axial position. A key advantage is that the spring element can be manufactured simply and with high precision from a single piece of round wire. This allows for the arrangement of several identically shaped spring elements around the circumference, enabling precise centering and alignment of the gear element. This results in backlash-free operation and therefore high precision.

[0025] In an advantageous embodiment, the yoke area is arranged at a first axial position, and the bracket areas extend from the first to the second axial position. It is advantageous that the spring element clamps onto the toothed portion axially in front of and behind the toothing.

[0026] In an advantageous embodiment, the toothing is a straight toothing. An advantage here is that the brake pad carrier is axially displaceable, particularly without rotation.

[0027] In an advantageous embodiment, further spring parts, identical and / or similarly designed to the spring part, are arranged around the circumference of the toothed part, in particular at the same radial distance and / or regularly and / or uniformly spaced from one another in the circumferential direction. The advantage here is that the improved centering enables reliable operation.

[0028] In a preferred embodiment, the brake pad carrier is made of a softer material than the drive pin. The advantage here is that the spring element prevents play between the toothed parts, thus reducing wear.

[0029] In a preferred embodiment, the drive element is made of metal, particularly steel. This offers the advantage of low wear, resulting in a long service life and extended operation.

[0030] Further advantages arise from the sub-claims.

[0031] The invention will now be explained in more detail with reference to schematic illustrations: In the Figure 1 A spring component, in particular a spring clip, is shown in an oblique view. Figure 2 A driver 20 of an electromagnetically actuated brake with spring element according to the invention is shown. In the Figure 3 is an excerpt of Figure 2 Shown enlarged. Figure 4 Figure 1 shows an alternative embodiment in which the spring part is mounted on the internal teeth of the brake pad carrier 23 instead of on the driver 20 and is supported on annular grooves 21 of the brake pad carrier 23.

[0032] As in the Figures 2 to 4 As shown, a driver 20 has an external toothing onto which the spring part is attached.

[0033] The brake has a current-carrying coil, which is designed as a ring winding and is received in a particularly ring-shaped recess of a ferromagnetic magnet body.

[0034] A rotor shaft 22 of an electric motor is rotatably mounted relative to the magnet body. The driver 20 is designed as an externally toothed, ring-shaped body and is fitted onto the rotor shaft 22. The rotor shaft 22 is non-rotatably connected to the driver 20. Preferably, a keyway connection is used for this purpose.

[0035] A brake pad carrier 23 with its internal teeth is mounted onto the external teeth of the drive lug 20. Thus, the brake pad carrier 23 is connected to the drive lug 20 in a rotationally fixed but axially displaceable manner.

[0036] A ferromagnetic armature disk is arranged axially, i.e., in the direction of the rotation axis of the rotor shaft 22, between the brake pad carrier 23 and the magnet body with the coil. This armature disk is connected to the magnet body in a rotationally fixed but axially displaceable manner. For this purpose, axially extending bolts are preferably fastened in the magnet body, which protrude through holes in the armature disk.

[0037] When the coil is not energized, the armature disk is pressed towards the brake pad carrier 23 by a spring force generated by spring elements supported on the magnet body, so that the latter is pressed against a braking surface. This preferably finely machined braking surface is formed either on a bearing flange of the electric motor, in which a bearing rotatably supports the rotor shaft 22 is received, or on a sheet metal part non-rotatably connected to the magnet body. The brake thus engages when the coil is not energized.

[0038] When the coil is energized, the armature disk is pressed towards the magnet body against the spring force generated by the spring elements, thus releasing the brake pad carrier 23. When energized, the brake is therefore released.

[0039] The teeth of the internal toothing of the brake pad carrier 23 protrude into tooth gaps of the external toothing of the driver 20.

[0040] The drive pin 20 is made of metal, in particular steel. The brake pad carrier 23 is made of a softer material than the drive pin 20, in particular a resin.

[0041] To reduce noise emissions caused by rattling of the two toothed sections, the spring part is attached to the outer toothing of the driver 20.

[0042] The spring part has two stirrup areas 1 which are connected via a yoke area 3.

[0043] The yoke area 3 is thus arranged between the two stirrup areas 1 and connected to both stirrup areas 1.

[0044] At the end of each ironing area 1 facing away from the yoke area 3, a respective end area 2 borders.

[0045] The respective bracket section 1 is inserted into a respective tooth gap of the external teeth of the driver 20. Due to a slight curvature of the respective bracket section 1, the area of ​​the bracket section 1 closest to the internal teeth presses against the head of a tooth of the internal teeth, which projects into the tooth gap that receives the bracket section 1.

[0046] At least by means of the yoke area 3, which engages in a circumferential annular groove of the driver 20, the spring part is supported on the driver 20 and presses on the respective tooth head of the internal toothing by means of a spring force generated by elastic deflection of the spring part.

[0047] The annular axis of the first annular groove 21 is aligned coaxially with the axis of rotation of the rotor shaft 22. The first annular groove 21 opens in a direction parallel to the axial direction. The groove walls thus limit the annular groove volume in the radial direction and opposite to the radial direction, respectively.

[0048] A second annular groove is provided on the driver 20 on the side facing away from the first annular groove 21. The annular axis of this second annular groove is also aligned coaxially with the axis of rotation of the rotor shaft 22. The second annular groove opens in the opposite direction to the axial direction. The groove walls of the second annular groove thus limit its annular groove volume in the radial direction and in the opposite direction to the radial direction.

[0049] The groove opening of the first annular groove 21 is therefore oriented in the opposite direction to the groove opening of the second annular groove.

[0050] The second ring groove is coaxial, i.e. parallel, aligned to the first ring groove 21 and has the same ring diameter and the same ring axis.

[0051] The end regions 2 engage in the second annular groove with elastic preload.

[0052] The spring part is shaped in such a way that it is elastically pre-tensioned when placed on the external toothing, and thus the stirrup area 3 and the end areas 2 are elastically pre-tensioned to each other and clamp the spring part onto the driver 20.

[0053] By clamping the spring part axially to the driver 20, the spring part is positively connected to the driver 20 in a radial direction.

[0054] The spring component is manufactured as a bent part from a single wire and preferably has the same wire cross-section throughout. This makes it simple and inexpensive to produce.

[0055] The first annular groove 21 and the second annular groove are arranged at a smaller radial distance to the axis of rotation of the rotor shaft 22 and / or the driver 20 than the smallest radial distance of the respective tooth gap in which the respective bracket area 1 is received.

[0056] In particular, the first annular groove 21 is formed in a first flat surface region of the driver 20, the normal direction of which is aligned parallel to the axial direction. The second annular groove is also formed in a second flat surface region of the driver 20, which is aligned parallel to the first surface region and / or axially spaced from the first surface region.

[0057] In further embodiments according to the invention, several of the aforementioned spring parts are mounted on the external teeth, wherein the spring parts are spaced apart from each other in the circumferential direction.

[0058] In further embodiments of the invention, the spring part is not mounted on the external teeth of the driver 20, but on the internal teeth of the brake pad carrier 23, as shown in Figure 4 shown. The first and second annular grooves are then arranged on the brake pad carrier 23, in particular being open in opposite directions to each other and aligned coaxially to each other, and arranged at the same radial distance. Reference symbol list

[0059] 1. Bracket area 2. End area 3. Yoke area 20. Drive pin 21. Ring groove 22. Shaft, especially rotor shaft 23. Brake pad carrier

Claims

1. A braking arrangement with a toothed part having gearing, and with at least one spring part, wherein the spring part has a yoke region which is connected to a first bow region (1) of the spring part which is connected at its end remote from the yoke region to a first end region (2) of the spring part, wherein the spring part is mounted on the gearing such that - the first bow region (1) of the spring part is arranged at least partially in a tooth space of the gearing, characterised in that the spring part is furthermore mounted on the gearing such that - the yoke region (3) engages in a first annular groove (21) formed on the toothed part, in particular on a first end face of the toothed part, - the first end region (2) engages in a second annular groove (21) formed on the toothed part, in particular formed on the other end face of the toothed part, in particular with the first annular groove (21) being a groove which is formed in the toothed part and which partially or entirely encircles the axis of rotation of the toothed part, in particular with the second annular groove (21) being a groove which is formed in the toothed part and which partially or entirely encircles the axis of rotation of the toothed part.

2. A braking arrangement according to claim 1, characterised in that a second bow region (1), spaced apart from the first bow region (1), of the spring part is connected to the yoke part, which bow region is connected at its end remote from the yoke part to a second end region (2) of the spring part, - the second bow region (1) of the spring part is arranged at least partially in a second tooth space of the gearing, - the second end region (2) engages in the second annular groove (21) formed on the toothed part.

3. A braking arrangement according to one of the preceding claims, characterised in that the first annular groove (21) is formed in a flat surface region of the toothed part, the normal vector of which is oriented parallel to the axial direction, with the ring axis of the first annular groove (21) being the same as the axis of rotation of the toothed part, in particular with the groove opening of the first annular groove (21) being opened towards the axial direction, in particular with the annular groove (21) being embodied uninterrupted around the axis of rotation in the circumferential direction.

4. A braking arrangement according to one of the preceding claims, characterised in that the second annular groove (21) is formed in a second flat surface region of the toothed part, the normal vector of which is oriented parallel to the axial direction, with the ring axis of the second annular groove (21) being the same as the axis of rotation of the toothed part.

5. A braking arrangement according to one of the preceding claims, characterised in that the gearing is external gearing, and the radial distance region which is covered by the first and second annular grooves (21) and is relative to the axis of rotation of the toothed part is spaced apart from the radial distance region covered by the gearing and / or is arranged radially within the radial distance region covered by the gearing, in particular with the toothed part being embodied as a driving element (20).

6. A braking arrangement according to one of claims 1 to 4, characterised in that the gearing is internal gearing, and the radial distance region which is covered by the first and second annular grooves (21) and is relative to the axis of rotation of the toothed part is spaced apart from the radial distance region covered by the gearing and / or is arranged radially outside the radial distance region covered by the gearing, in particular with the toothed part being embodied as a brake lining carrier (23).

7. A braking arrangement according to one of the preceding claims, characterised in that the braking arrangement has a shaft (22), in particular rotor shaft of an electric motor, with a driving element (20) being mounted on the shaft (22) and connected non-rotatably to the shaft (22), with a brake lining carrier (23) being mounted on the driving element (20) and internal gearing of the brake lining carrier (23) meshing with external gearing of the driving element (20), so that the brake lining carrier (23) is connected non-rotatably to the driving element (20) but is arranged axially displaceably relative to the driving element (20), with the driving element (20) forming the toothed part or the brake lining carrier (23) forming the toothed part.

8. A braking arrangement according to one of the preceding claims, characterised in that the braking arrangement has a magnet body, in particular ferromagnetic magnet body, in which an energisable coil, in particular coil winding, is received, with the shaft (22) being rotatably borne, in particular relative to the magnet body, by means of bearings received in a housing part, in particular bearing flange, with a ferromagnetic armature disc being arranged axially between the brake lining carrier (23) and the magnet body, with the armature disc being connected non-rotatably to the magnet body but being arranged axially displaceably, in particular relative to the magnet body, with, when the coil is energised, the armature disc being drawn towards the magnet body counter to the spring force generated by spring elements which are supported on the magnet body, and when the coil is not energised the armature disc being pressed by the spring elements onto the brake lining carrier (23) such that the brake lining carrier (23) is pressed onto a braking face arranged on that side of the brake lining carrier (23) which is remote from the armature disc, in particular with the braking face - either being formed on a bearing flange of the electric motor, with a bearing which rotatably bears the rotor shaft being received in the bearing flange and the bearing flange being connected non-rotatably to the magnet body, - or being formed on a sheet-metal part connected non-rotatably to the magnet body.

9. A braking arrangement according to one of the preceding claims, characterised in that the first bow region (1) which is supported on the first annular groove (21) is elastically deflected such that the first bow region (1) presses, in particular presses in the radial direction, on a first tooth tip of the gearing of a second toothed part, with the gearing of the second toothed part meshing with the gearing of the first toothed part and / or in that the second bow region (1) which is supported on the second annular groove (21) is elastically deflected such that the second bow region (1) presses, in particular presses in the radial direction, on a second tooth tip of the gearing of a second toothed part with the gearing of the second toothed part meshing with the gearing of the first toothed part.

10. A braking arrangement according to one of the preceding claims, characterised in that the spring part is produced as a bent part from round wire.

11. A braking arrangement according to one of the preceding claims 2 to 10, characterised in that the two end regions (2) of the spring part are spaced apart from each other in the circumferential direction and / or are arranged at the same second axial position.

12. A braking arrangement according to claims 11 and 2, characterised in that the yoke region (3) is arranged at a first axial position and the bow regions (1) extend from the first to the second axial position.

13. A braking arrangement according to one of the preceding claims, characterised in that the gearing is spur toothing.

14. A braking arrangement according to one of the preceding claims, characterised in that further spring parts which are configured identically to and / or in the same manner as the spring part are arranged on the circumference of the toothed part, in particular at the same radial distance and / or regularly and / or uniformly spaced apart from each other in the circumferential direction.

15. A braking arrangement according to one of the preceding claims 7 to 13, characterised in that the brake lining carrier (23) is made from a softer material than the driving element (20) and / or in that the driving element (20) is made of metal, in particular of steel.