Brake assembly, in particular of a brake motor, for braking a shaft, in particular a rotor shaft of the brake motor

Abstract

A brake assembly for braking a shaft, the brake assembly having a brake lining carrier (1), a first radial spacing region (21) of the brake lining carrier being arranged radially outside a second radial spacing region (22) of the brake lining carrier and abutting said second radial spacing region, the second radial spacing region being arranged radially outside a third radial spacing region (23) of the brake lining carrier and abutting said third radial spacing region, a brake lining (20) being integrally bonded on both sides in the first radial spacing region on the brake lining carrier, the brake lining carrier having an internal tooth system in the third radial spacing region, the centre of gravity of said internal tooth system having an offset axially at the common centre of gravity of the two brake linings.

Description

[0001] Braking arrangement, in particular of a brake motor, for braking a shaft, in particular rotor shaft of the brake motor

[0002] Description:

[0003] The invention relates to a braking arrangement, in particular a brake motor, for braking a shaft, in particular the rotor shaft of the brake motor.

[0004] It is generally known that a braking arrangement is designed to slow down a shaft and is made up of many parts.

[0005] From DE 102022004107 A1, a brake arrangement is known as the closest prior art.

[0006] A spring-applied brake is known from DE 102006010656 B3.

[0007] A brake arrangement is known from DE 102023001 338 A1.

[0008] Figure 3 of DE 102022001 345 A1 shows a brake pad carrier whose axial wall thickness has a single local maximum in the radial direction, which is radially spaced from the radial edges of the brake pad carrier. This is because the second maximum opens into the radial outer circumference and is therefore not spaced from this radial edge.

[0009] The invention is therefore based on the objective of making a brake arrangement cost-effective to manufacture.

[0010] According to the invention, the problem is solved in the brake arrangement according to the features specified in claim 1 and in the brake motor according to the features specified in claim 15.

[0011] Important features of the invention in the brake arrangement, in particular of a brake motor, for braking a shaft, in particular rotor shaft of the brake motor, are that the brake arrangement has a brake pad carrier, in particular annular and / or perforated disc-shaped,

[0012] ISI \ EIDOPAT 08.12.2025 in particular wherein the brake pad carrier has internal teeth,

[0013] wherein a first radial spacing region of the brake pad carrier is arranged radially outside a second radial spacing region of the brake pad carrier and adjoins this second radial spacing region,

[0014] wherein the second radial spacing area is arranged radially outside a third radial spacing area of ​​the brake pad carrier and adjoins this third radial spacing area,

[0015] wherein a brake pad is axially bonded to both sides of the brake pad carrier in the first radial spacing area, in particular by adhesive bonding,

[0016] wherein the brake pad carrier has an internal toothing in the third radial spacing area, the center point or center of gravity of which, in particular axial, is offset in the axial direction to the common center point or center of gravity of the two brake pads.

[0017] A key advantage is the cost-effective manufacturing of the brake assembly. The brake pad carrier is stackable because the internal teeth are axially offset, allowing identical brake pad carriers to be stacked and stored, thus requiring only a small and therefore cost-effective storage volume. Furthermore, the brake pad carrier can be manufactured as a single piece. In addition, the increasing wall thickness towards the radial center allows for the transmission of a high braking torque to the shaft, as progressively higher forces can be transmitted with decreasing radial distance. In particular, the internal teeth are subjected to only a low Hertzian contact stress.

[0018] In an advantageous embodiment, the maximum axial width of the brake pad carrier in the first radial spacing range is smaller than the maximum axial width of the brake pad carrier in the second radial spacing range. This is advantageous because a high braking torque can be transmitted from the brake pads to the shaft.

[0019] In an advantageous embodiment, the maximum axial width of the brake pad carrier in the second radial spacing range is smaller than the maximum axial width of the brake pad carrier in the third radial spacing range. This is advantageous because a high braking torque can be transmitted from the brake pads to the shaft. In an advantageous embodiment, the radial spacing is referenced to the axis of rotation of the shaft. It is advantageous that the axial direction is aligned parallel to the axis of rotation of the shaft and that the circumferential direction is also referenced to the axis of rotation of the shaft.

[0020] In a preferred embodiment, the respective brake pad is designed as a ring-shaped and / or perforated disc-shaped stamped part. The advantage here is that cost-effective production of the brake pads is possible.

[0021] In an advantageous embodiment, the brake pad carrier has a flat surface, in particular an annular surface, on both axial sides in the first radial spacing region, against which a respective brake pad rests, and is in particular bonded, especially by adhesive. It is advantageous that a flat surface section of the brake pad carrier acts as the adhesive surface.

[0022] In a preferred embodiment, the teeth of the internal gearing are rounded at the ends, particularly for threading onto an external gear. This design offers the advantage of quick, simple, and cost-effective manufacturing.

[0023] In an advantageous embodiment, the axial width of the brake pad carrier increases monotonically, and in particular strictly monotonically, with increasing radial distance in the first radial spacing range.

[0024] In particular, the axial width of the brake pad carrier increases proportionally to the increasing radial spacing in the first radial spacing range. An advantage of this is that a high braking torque can be transmitted from the brake pads to the shaft.

[0025] In an advantageous embodiment, the axial width of each brake pad is independent of the radial spacing. A further advantage is that markings can be provided.

[0026] In an advantageous embodiment, the brake pad carrier has a marking in the second radial spacing area. An advantage here is that identification information can be applied. In another advantageous embodiment, the brake pad carrier has an axially forward-projecting projection in the third radial spacing area, which can be inserted into a recess created by the offset of the brake pad carrier in the third radial spacing area of ​​a second brake pad carrier that is structurally identical and / or identical to the brake pad carrier.

[0027] In particular, the projection features internal teeth. An advantage is that the brake pad carrier is stackable, thus making cost-effective use of storage space.

[0028] In an advantageous embodiment, the brake pad carrier has an axially forward-directed recess in the radial area covered by the projection,

[0029] in particular where the maximum axial height of the projection equals the maximum axial depth of the retraction,

[0030] In particular, the radial width of the projection equals the radial width of the retraction. It is advantageous that the brake pad carrier is stackable.

[0031] In an advantageous embodiment, the brake pad carrier has axially oriented recesses spaced apart from one another in the circumferential direction in the first and second radial spacing regions. This is advantageous because it allows for material savings and the absorption of excess adhesive.

[0032] In an advantageous embodiment, the brake pad carrier is mounted on a drive element that is non-rotatably connected to the shaft.

[0033] wherein the internal toothing engages with an external toothing of the drive, wherein the brake pad carrier is arranged to be axially movable,

[0034] wherein a ring winding is received in a recess, in particular annular groove, of a magnetic body of the brake assembly,

[0035] wherein an armature disk, which is fixedly connected to the magnet body and arranged to be axially movable, is arranged axially between the brake pad carrier and the magnet body, wherein spring elements supported on the magnet body press against the armature disk,

[0036] wherein a part having a braking surface, in particular a finely machined surface, is arranged on the side of the brake pad carrier facing away from the armature disc, in particular wherein the part is firmly connected to the magnet body, in particular via axially aligned bolts which project through recesses in the armature disc. It is advantageous that, when the ring winding is not energized, the spring elements press the armature disc towards the brake pad carrier and thus push and press the latter onto the braking surface. When the ring winding is energized, however, the armature disc is pulled towards the magnet body against the spring force generated by the spring elements, so that no braking torque is generated.

[0037] In an advantageous embodiment, a spring clip, elastically connected to the internal teeth of the brake pad carrier, is elastically supported on the external teeth of the drive pin. An advantage of this is that rotational play between the drive pin and the brake pad carrier is prevented.

[0038] In an advantageous embodiment, the axial width of the brake pad carrier has at least two local maxima in the radial direction, each radially spaced from the two radial edges of the brake pad carrier. The advantage here is that, firstly, the brake pads can be radially centered due to the first local maximum, and secondly, a spring clip can be attached, or stackability can be ensured in other circumferential regions by means of an axial projection.

[0039] Important features of the brake motor, comprising an electric motor with the aforementioned brake arrangement, are that the rotor shaft is rotatably mounted via a first bearing, which is received in a bearing shield of the electric motor, and via a second bearing, which is received in a bearing flange of the electric motor.

[0040] The bearing shield acts as the part containing the braking surface. An advantage of this design is that the braking mechanism is integrated into the brake motor.

[0041] Further advantages arise from the dependent claims. The invention is not limited to the combination of features of the claims. For those skilled in the art, further meaningful combinations of claims and / or individual claim features and / or features of the description and / or the figures will become apparent, in particular from the problem statement and / or the problem arising from a comparison with the prior art. The invention will now be explained in more detail with reference to a schematic diagram:

[0042] Figure 1 shows a longitudinal section through a brake motor according to the invention, comprising an electric motor and an electromagnetically actuated brake arrangement.

[0043] Figure 2 shows a longitudinal section through the brake arrangement, comprising a brake pad carrier 1 according to the invention.

[0044] Figure 3 shows an area of ​​the brake motor containing the brake pad carrier 1.

[0045] Figure 4 shows a top view of the brake pad carrier 1.

[0046] Figure 5 shows an enlarged section of Figure 4.

[0047] Figure 6 shows several identical brake pad carriers 1 arranged one behind the other in an axial direction on a driver 9, in an oblique view.

[0048] Figure 7 shows a sectional view of two brake pad carriers 1 arranged one behind the other.

[0049] As shown in the figures, the brake motor has an electric motor and an electromagnetically actuated brake assembly arranged on the electric motor.

[0050] The rotor shaft 6 of the electric motor is rotatably mounted via a first bearing 12, which is received in a bearing shield 9, and a second bearing 13, which is received in a bearing flange 11.

[0051] A stator housing 14 of the electric motor, enclosing the stator winding 10, is arranged between the bearing flange 11 and the bearing shield 9. A magnet body 5, in particular ferromagnetic, has an annular groove into which a ring winding 3, received in a coil carrier 4, is inserted, the ring axis of which is aligned coaxially with the axis of rotation of the rotor shaft 6.

[0052] A ring-shaped driver is connected to the rotor shaft 6 in a rotationally fixed manner, in particular via a keyway connection. The key 7 of the keyway connection projects into both an axial groove of the rotor shaft 6 and an axial groove of the driver 8. The driver 8 has external teeth which engage with internal teeth of a brake pad carrier 1, in particular a disc-shaped one, mounted on the driver 8. Thus, the brake pad carrier 1 is rotationally fixed to the driver 8.

[0053] Thus, the brake pad carrier 1 is connected to the driver in a rotationally fixed and axially movable manner.

[0054] An armature disk arranged axially between the magnet body 5 and the brake pad carrier 1 is rotationally fixed to the magnet body 5 and axially movable. Preferably, bolts attached to the magnet body 5 and / or screwed into threaded bores in the magnet body project through recesses in the armature disk 2.

[0055] The armature disk is preferably made of ferromagnetic material and, when the ring winding 3 is energized, is pulled towards the magnet body 5 against the spring force generated by spring elements supported on the magnet body 5.

[0056] The magnetic body 5 is firmly connected to the bearing shield 9.

[0057] The brake pad carrier 1 covers a first radial spacing area 21 in the radial direction, to which a second radial spacing area 22 is connected radially inwards, to which a third radial spacing area 23 is connected radially inwards.

[0058] The maximum axial width of the third radial spacing range 23 is greater than the maximum width of the second radial spacing range 22, which in turn is greater than the maximum axial width of the first radial spacing range 21.

[0059] The internal toothing of the brake pad carrier 1 is machined into the brake pad carrier 1 in the third radial spacing area 23. The end face of the brake pad carrier 1 has a marking in the second radial spacing area 22. In particular, the brake pad carrier 1 in the second radial spacing area 22 is provided with a flat surface, in particular an annular surface, which has a marking that is clearly recognizable from a distance without visual aids.

[0060] On the radial outer side of the second radial spacing area 22, radially directed centering projections 50 are formed spaced apart from each other in the circumferential direction, which position the brake pads 20 which are glued onto the first radial spacing area 21, in particular on both sides.

[0061] As can be seen in Figure 5, the centering projections 50 protrude in a radial direction and contact the brake pad 20 which is bonded to the brake pad carrier 1. Since the bonding surface between the brake pad 20 and the brake pad carrier 1 is flat and has a normal direction that is aligned parallel to the axial direction, the radial positioning and centering is achieved solely via the radial centering projections 50.

[0062] Each brake pad 20 is ring-shaped and / or disc-shaped and is glued to the end face of the brake pad carrier 1 in the first radial spacing area 21.

[0063] In the first radial spacing region 21, the brake pad carrier 1 is conically shaped. For this purpose, the axial width of the brake pad carrier 1 increases monotonically, and in particular strictly monotonically, with increasing radial spacing, especially towards the radial outside.

[0064] In this way, reduced wear during operation can be achieved, especially since linear contact is possible.

[0065] In the first and second radial spacing areas (21, 22) of the brake pad carrier 1, axially directed recesses spaced apart from each other in the circumferential direction are formed.

[0066] A spring clip 24, elastically connected to, in particular clamped to, the internal teeth of the brake pad carrier 1, is elastically supported on the external teeth of the driver 8 and thus prevents rotational play between the driver 8 and the brake pad carrier 1. In the third radial spacing region 23, an axially directed recess is formed on the axially front end face of the brake pad carrier 1, in particular in the radially inner end region of the third radial spacing region 23. An axially directed projection is formed on the axially rear end face of the brake pad carrier 1.

[0067] Thus, the center of gravity of the internal toothing has an axial offset to the center of gravity of the first radial spacing area 21, the second radial spacing area 22, as well as to the radially outside the aforementioned radially inner end area of ​​the third radial spacing area 23.

[0068] In particular, the center of gravity of the internal toothing has an axial offset relative to the center of gravity of the brake pads 20. The two brake pads 20 are identical to each other, designed as perforated discs and / or rings, whose ring axis is coaxially aligned with each other.

[0069] Preferably, the area covered in the axial direction by a first of the two brake pads 20 includes the area covered in the axial direction by the internal toothing of the third radial spacing area 23, but not the area covered in the axial direction by the second of the two brake pads 20.

[0070] The brake pad carrier 1 shaped in this way is therefore stackable. This is because the axially projecting internal toothing on one side can be inserted into the recess created by the offset on the other side of another, identically shaped brake pad carrier 1, as can be seen in Figure 7, whereby the brake pads 20 still present there can be disregarded, thus enabling axial insertion of the second brake pad carrier 1 into the first.

[0071] The fact that two local maxima of the axial wall thickness of the brake pad carrier 1 are formed in the radial direction enables, on the one hand, the axial protrusion of the internal toothing to project into the recess of the other brake pad carrier 1, and on the other hand, one of the local maxima enables the creation of a radial shoulder for centering the brake pads 20.

[0072] In further embodiments of the invention, the tooth edges of the internal toothing are provided with an insertion chamfer, so that the internal toothing is threaded into the drive toothing when the brake pad carrier 1 is pushed onto the drive 8 during assembly of the brake assembly. Reference numeral list

[0073] 1 brake pad carrier

[0074] 2 Anchor disc

[0075] 3 ring winding

[0076] 4 coil carriers

[0077] 5 Ferromagnetic magnet bodies 6 Rotor shaft

[0078] 7 Key

[0079] 8 ring-shaped drive lugs

[0080] 9 Storage sign

[0081] 10 Stator winding

[0082] 11 Bearing flange

[0083] 12 first camp

[0084] 13 second camp

[0085] 14 Stator housings

[0086] 20 brake pads

[0087] 21 First radial spacing range 22 Second radial spacing range 23 Third radial spacing range 24 Spring clip

[0088] 50 radial centering projection

Claims

Patent claims:

1. Braking arrangement, in particular of a brake motor, for braking a shaft, in particular the rotor shaft of the brake motor, wherein the brake assembly has a brake pad carrier, in particular annular and / or perforated disc-shaped, in particular wherein the brake pad carrier has internal teeth, characterized by the fact that a first radial spacing area of ​​the brake pad carrier is arranged radially outside a second radial spacing area of ​​the brake pad carrier and borders on this second radial spacing area, wherein the second radial spacing area is arranged radially outside a third radial spacing area of ​​the brake pad carrier and adjoins this third radial spacing area, wherein a brake pad is axially bonded to both sides of the brake pad carrier in the first radial spacing area, in particular by adhesive bonding, wherein the brake pad carrier has an internal toothing in the third radial spacing region, the center point or center of gravity of which, in particular its axial center point, is offset in the axial direction from the common center point or center of gravity of the two brake pads.

2. Brake arrangement according to claim 1, characterized by the fact that the maximum axial width, in particular wall thickness, of the brake pad carrier in the first radial spacing range is smaller than the maximum axial width of the brake pad carrier in the second radial spacing range.

3. Brake arrangement according to one of the preceding claims, characterized by the fact that the maximum axial width, in particular wall thickness, of the brake pad carrier in the second radial spacing range is smaller than the maximum axial width of the brake pad carrier in the third radial spacing range.

4. Brake arrangement according to one of the preceding claims, characterized by the fact that radially oriented centering projections (50) are formed on the radial outer side of the second radial spacing area, spaced apart from each other in the circumferential direction, which position the brake pads (20) which are bonded to the first radial spacing area (21), in particular on both sides, and / or that the radial distance is relative to the axis of rotation of the shaft.

5. Brake arrangement according to one of the preceding claims, characterized by the fact that the respective brake pad is designed as a ring-shaped and / or perforated disc-shaped stamped part.

6. Brake arrangement according to one of the preceding claims, characterized by the fact that The brake pad carrier has a flat surface, in particular annular surface, on both sides axially in the first radial spacing area, against which a respective brake pad rests, in particular and is materially bonded, in particular glued.- 14- 7. Brake arrangement according to one of the preceding claims, characterized by the fact that The teeth of the internal toothing are rounded on the front side, especially for threading onto an external toothing.

8. Brake arrangement according to one of the preceding claims, characterized by the fact that the axial width of the brake pad carrier in the first radial spacing range increases monotonically, and in particular strictly monotonically, with increasing radial spacing, in particular where the axial width of the brake pad carrier in the first radial spacing range increases proportionally to the increasing radial spacing, and / or that the axial width of the brake pad carrier has at least two local maxima in the radial direction, each radially spaced from the two radial edges of the brake pad carrier.

9. Brake arrangement according to one of the preceding claims, characterized by the fact that the axial width of the respective brake pad is independent of the radial spacing, and / or the brake pad carrier has a marking in the second radial spacing area.- 15- 10. Brake arrangement according to one of the preceding claims, characterized by the fact that The brake pad carrier has a forward-projecting axial projection in the third radial spacing area, which can be inserted into a recess created by the offset of the brake pad carrier in the third radial spacing area of ​​a second brake pad carrier that is structurally identical and / or identical to the brake pad carrier. in particular where the projection has internal teeth.

11. Brake arrangement according to one of the preceding claims, characterized by the fact that the brake pad carrier in the radial area covered by the projection exhibits a forward-directed retraction, in particular where the maximum axial height of the projection equals the maximum axial depth of the retraction, in particular where the radial width of the projection is equal to the radial width of the retraction.

12. Brake arrangement according to one of the preceding claims, characterized by the fact that In the first and second radial spacing regions (21, 22), the brake pad carrier 1 has axially oriented recesses spaced apart from each other in the circumferential direction.- 16- 13. Brake arrangement according to one of the preceding claims, characterized by the fact that the brake pad carrier is mounted on a drive wheel connected to the shaft, wherein the internal toothing engages with an external toothing of the drive, wherein the brake pad carrier is arranged to be axially movable, wherein a ring winding is received in a recess, in particular annular groove, of a magnetic body of the brake assembly, wherein an armature disk, rotatably connected to the magnet body and arranged to be axially movable, is arranged axially between the brake pad carrier and the magnet body, where spring elements supported on the magnet body press against the armature disc, wherein a part having a braking surface, in particular a finely machined surface, is arranged on the side of the brake pad carrier facing away from the armature disc, in particular wherein the part is firmly connected to the magnetic body, in particular via axially aligned bolts which protrude through recesses in the armature disc.

14. Brake arrangement according to one of the preceding claims, characterized by the fact that a spring clip, elastically connected to the internal teeth of the brake pad carrier, in particular clamped to it, is elastically supported on the external teeth of the drive pin.- 17- 15. Brake motor comprising an electric motor with a brake arrangement according to one of the preceding claims, characterized by the fact that the rotor shaft is rotatably mounted via a first bearing, which is housed in a bearing shield of the electric motor, and via a second bearing, which is housed in a bearing flange of the electric motor. where the bearing shield functions as the part containing the braking surface.

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