Brake assembly and electric motor comprising a brake assembly

Abstract

The invention relates to a brake assembly, particularly of an electric motor, wherein the brake assembly comprises an annular driving element and a lining carrier, the lining carrier having an inner toothing which is placed upon an outer toothing of the driving element, the brake assembly having an annular spring arranged between the driving element and the lining carrier, and the annular spring being supported in a groove and lying on tooth tips of one of the two toothings.

Description

[0001] Brake arrangement and electric motor with brake arrangement

[0002] Description:

[0003] The invention relates to a brake arrangement and an electric motor with a brake arrangement.

[0004] It is generally known that a brake assembly comprises a pad carrier having brake pads.

[0005] From DE 10 2022 001 345 A1, a shaft-hub connection is known as the closest prior art.

[0006] A toothed coupling with a spring is known from DE 10 2011 121 790 A1.

[0007] A centering device for pinions is known from DE 78 25 113 U 1.

[0008] From DE 10 2006 010 656 B3 a spring-pressure brake with a brake disc having friction surfaces on opposite sides is known.

[0009] From DE 10 2017 104 598 A1 a shaft-hub connection with radially outward-pointing securing hooks on a spring plate is known.

[0010] The invention is therefore based on the object of designing a safe operation of a brake arrangement and of an electric motor comprising the brake arrangement.

[0011] According to the invention, the object is achieved in the brake arrangement according to the features specified in claim 1 and in the electric motor according to the features specified in claim 15.

[0012] Important features of the invention in the brake arrangement, in particular of an electric motor, are that the brake arrangement has an annular driver and a lining carrier, wherein the lining carrier has an internal toothing which is placed on an external toothing of the driver, in particular such that the lining carrier is connected to the driver in a rotationally fixed manner and is arranged to be movable axially, in particular parallel to the direction of the ring axis of the driver, relative to the driver, wherein the brake arrangement has an annular spring arranged between the driver and the lining carrier, in particular an annular spring extending in the circumferential direction, wherein the annular spring is supported in a groove, in particular at the groove base of the groove, wherein the annular spring rests on tooth tips of one of the two toothings, in particular on tooth tips of the internal toothing or the external toothing.

[0013] The advantage of this is that safe operation of the brake assembly can be achieved. In particular, brake release can be reliably ensured because the annular spring is elastically deflected in the axial direction by the brake pad carrier when the brake is applied and then causes or at least assists in the resetting of the pad carrier when the brake is released. In particular, the elastically deflected annular spring, which relaxes during release, supports the lifting of the pad carrier from the braking surface.

[0014] This behavior of the annular spring is achieved by the fact that, on the one hand, the annular spring is supported radially in the groove and thus axially limited, and, on the other hand, it rests radially so firmly on the tooth tips that the annular spring is not displaced in the axial direction on the respective tooth tip, but remains sufficiently fixed to the tooth tip by static friction. In this way, it is reliably ensured that when the brake assembly is engaged, in particular activated, the annular spring is elastically deflected. When the brake is released, this elastic deflection is reduced, so that the brake pad carrier, with its brake pads facing the braking surface, is pulled away from the braking surface, in particular by relaxing the annular spring.

[0015] In an advantageous embodiment, the annular spring is polygonal, in particular regularly polygonal, in shape. This is advantageous in that well-defined support points and bearing points are provided. In particular, these respective points are spaced apart from each other in the circumferential direction, in particular regularly spaced. This spacing creates a lever arm between the respective support point and the two adjacent bearing points, which ensures a well-defined restoring force for pulling the pad carrier away from the braking surface.

[0016] The circumferential direction, the radial direction and the axial direction are each related to the axis of rotation of the driver, the lining carrier and / or the shaft connected to the driver in a rotationally fixed manner, in particular the rotor shaft of the electric motor.

[0017] In an advantageous embodiment, the annular spring is formed from a wire, in particular round wire and / or flexible wire, with a polygonal bent shape. This is advantageous because it allows for simple manufacturing.

[0018] In an advantageous embodiment, the annular spring is made of round wire. The advantage here is that the annular spring is easy to manufacture as a bent part.

[0019] In an advantageous embodiment, the annular spring is made of spring steel. This is advantageous because the annular spring has a sufficiently large range for elastic deflection and is therefore not inelastically deformed in the operating range. The operating range encompasses the deflection that the brake lining carrier assumes between the released and applied states of the brake assembly.

[0020] In an advantageous embodiment, the groove is designed as an internal groove in the lining carrier, in particular in a base ring of the lining carrier, and the annular spring rests on tooth tips of the external toothing, in particular wherein the groove is arranged in the axial direction in front of or behind the internal toothing of the lining carrier and the area covered by the external toothing in the axial direction comprises the area covered by the groove in the axial direction. The advantage here is that the annular spring is supported radially outside the contact points on the tooth tips. This means that the positive fit in the groove is realized at a greater radial distance than the non-positive fit on the tooth tips. In addition, the production of the groove is very simple because it is not carried out within the toothing, but axially next to the toothing.In an alternative advantageous embodiment, the groove is designed as an external groove in the driver and the annular spring rests on tooth tips of the internal toothing, in particular wherein the groove is designed within the external toothing, in particular wherein the area covered by the groove in the axial direction is encompassed by the area covered by the external toothing in the axial direction, in particular wherein the area covered by the internal toothing in the axial direction encompasses the area covered by the groove in the axial direction. The advantage here is that the groove has to be provided within the toothing, but the teeth of the toothing contribute to the axial limitation of the annular spring. The support here takes place radially within the support on the tooth tips of the internal toothing.

[0021] In an advantageous embodiment, the groove is V-shaped or has at least one inclined groove wall, in particular so that the annular spring executes a rotary movement upon axial movement of the lining carrier relative to the driver, wherein the pivot point of the rotary movement is arranged at the groove base of the groove and the wire thickness and / or the diameter of the wire, in particular round wire, from which the annular spring is made, is smaller than the groove width of the groove at the groove base of the groove, in particular wherein the annular spring rests against the inclined groove wall or against the groove wall of the V-shaped groove at maximum rotational deflection of the annular spring, in particular rests against it in a linear manner.

[0022] The advantage here is that the angled groove wall increases the degree of rotational freedom, especially the degree of tilting freedom, for the annular spring. Thus, when the lining carrier is axially displaced, the annular spring supported at the groove base is able to rotate a wider range than with a straight groove wall.

[0023] To accommodate the annular spring, the groove is wider than the thickness of the round wire from which the annular spring is made. In particular, the diameter of the round wire is smaller than the groove width, especially the width measured at the groove base. The angled groove wall thus allows for a wider rotation range of the annular spring, with the pivot point located at the groove base.

[0024] In an advantageous embodiment, one or two support plates are attached to the base ring, to which brake pads are attached, in particular to which brake pads are materially connected, in particular wherein the brake pads are spaced from one another, in particular regularly, in the circumferential direction. It is advantageous in this case that brake pads are attached to one side of the respective separating plate, so that brake pads are attached axially on both sides of the pad carrier. Manufacturing is simple because the two separating plates are placed as a stack on a radially protruding collar region of the base ring running around the circumference and are fastened by means of a screw screwed axially into the collar region. The brake pads are applied to the separating plates and arranged radially outside the base ring, in particular the collar region. In this way, the brake pads are protected from high forces.

[0025] In an advantageous embodiment, the brake pads are arranged radially outside the base ring. This is advantageous because the brake pads are mechanically protected, particularly from the fastening forces introduced by the screws. The brake pads are preferably bonded to the separating plates by a material bond, in particular adhesive bonding. Thus, the brake pads only have to transmit the friction torque generated when the brake assembly is applied, in particular activated, and are not subjected to any additional forces. Since the separating plates are more elastic than the base ring, manufacturing tolerances are compensated for or at least sufficiently offset by elastic deformation of the separating plates.

[0026] In an advantageous embodiment, the support plates are detachably connected to the base ring by means of axially directed screws, which are screwed into axially directed threaded holes in the base ring, in particular wherein the support plates are connected by the screw heads of the screws to a

[0027] The base part is formed on the base part, projects radially from the base part and is continuously formed in the circumferential direction. The advantage here is that the separating plates are pushed onto the base ring as an axially directed stack from the axial direction, and the stack is pressed towards the collar area by one or more screws, particularly in the circumferential direction by the screws, which are preferably regularly spaced from one another.

[0028] In an advantageous embodiment, the annular spring has a discontinuity at one point along its circumference. This is advantageous in that greater elasticity can be achieved and it can be easily manufactured as a bent wire part and easily assembled, particularly on the driver, by spreading the leg areas.

[0029] In an advantageous embodiment, the area covered by the annular spring in the circumferential direction is less than 360°. This is advantageous because the annular spring is interrupted at one point in the circumferential direction, thus achieving greater elasticity.

[0030] In an advantageous embodiment, the annular spring is arranged radially between the driver and the lining carrier, in particular the base ring, in the area covered by the annular spring in the axial direction. This advantageously centers the lining carrier relative to the driver, thus reducing noise emissions during operation, particularly when the shaft is rotating. In particular, rattling noises caused by circumferentially or radially directed relative vibrations can be suppressed. Furthermore, an axial restoring force can be provided for the lining carrier to retract it from the braking surface when the brake assembly is released.

[0031] In an advantageous embodiment, the polygon has an odd number of vertices, in particular seven. This is advantageous in that vibrations occurring in the circumferential direction can be suppressed more effectively, since the harmonics of a fundamental oscillation have an even number of nodes, making even-numbered harmonics easier to excite. However, the annular spring has an odd number of vertices and is therefore less easily excited to oscillate.

[0032] In an advantageous embodiment, the driver has a chamfer on its axial end region facing the lining carrier, in particular the base ring, prior to insertion into the lining carrier, such that the annular spring accommodated in the circumferential groove is expanded, in particular preloaded, when the driver is inserted into the lining carrier, in particular the base ring, and in particular rests with multiple contact points on the respective tooth tips of the gearing. The advantage here is that the annular spring is preloaded during axial insertion and is thus arranged between the driver and the lining carrier with sufficient slip protection.

[0033] In an advantageous embodiment, in the area covered by the chamfer in the axial direction, in particular parallel to the axis of rotation of the shaft and / or the driver, the outer diameter of the driver increases monotonically, in particular strictly monotonically, with increasing distance from the end face of the driver delimiting the chamfer, in particular wherein the largest outer diameter is independent of the axial position in the area axially spaced from the external toothing, in particular axially spaced from the chamfer. The advantage here is that the annular spring is preloaded during axially directed insertion and is thus arranged between the driver and the lining carrier in a manner that is sufficiently secured against slipping.

[0034] In an advantageous embodiment, the brake arrangement comprises a magnetic body in which an electrically energizable ring winding is accommodated, wherein the ring axis of the ring winding is aligned coaxially to the rotational axis of the shaft, wherein a ferromagnetic armature disk arranged axially between the ring winding and the lining carrier is connected to the magnetic body in a rotationally fixed manner and is arranged to be axially movable relative to the magnetic body, wherein the shaft is arranged to be rotatably mounted relative to the magnetic body, in particular wherein bolts fastened in the magnetic body are guided through recesses of the

[0035] Armature disk protrude axially, wherein spring elements supported on the magnetic body press onto the armature disk, in particular wherein the brake arrangement is designed such that when the annular winding is not energized, the armature disk is pressed towards the lining carrier by the spring elements, so that this lining carrier is pressed on its side facing away from the armature disk onto a braking surface which is formed on a friction plate or on a bearing shield of the electric motor, in particular which accommodates a bearing of the shaft, in particular wherein the brake arrangement is designed such that when the annular winding is energized, the armature disk is pulled towards the magnetic body against the spring force generated by the spring elements and axial play is thus made available to the lining carrier, so that a restoring force generated by the elastically deformed annular spring pulls the lining carrier back axially, in particular in the axial direction, from the braking surface.The advantage here is that in the event of a power failure, the brake automatically engages, thus achieving greater operational reliability, in particular the operational reliability of a drive arrangement protected by the brake arrangement.

[0036] A second braking surface is activated when the brake lining carrier and the armature plate come into contact. Thus, the brake lining carrier is in axial frictional contact on both sides when the brake is activated.

[0037] In an advantageous embodiment, when the toothing is designed as external toothing, the straight sides of the polygonally shaped annular spring each rest tangentially on the external toothing of the driver, in particular wherein a respective support point is arranged centrally in each of the sides and the corner regions of the polygonally shaped annular spring have the respective support points at which the annular spring is supported on the groove base of the groove, in particular wherein the corner regions each connect two of those sides of the polygon which are closest to one another. The advantage here is that a large lever arm can be achieved between the support point on the respective tooth tip and the associated support point. This enables the annular spring to be pressed firmly against the driver and the lining carrier.

[0038] In an advantageous embodiment, when the groove is designed as an inner groove, the support points are arranged on the inscribed inner circle of the polygon. This is advantageous because the support points are located in the center of each side, thus providing a sufficiently large lever arm to the nearest adjacent support point in the circumferential direction, so that upon axial displacement of the pad carrier toward the braking surface, a sufficiently high elastic preload is achieved to provide the restoring force effective when releasing the brake assembly.

[0039] In an advantageous embodiment, when the groove is designed as an outer groove, the support points are arranged on the circumscribed outer circle of the polygon. This is advantageous in that a sufficiently large lever arm is provided between the support points and the nearest support points in the circumferential direction, so that upon axial displacement of the pad carrier toward the braking surface, a sufficiently high elastic preload is achieved to provide the restoring force effective when releasing the brake assembly.

[0040] Important features of the electric motor with a brake assembly include the fact that the driver is mounted on a rotor shaft of the electric motor and is connected to the rotor shaft in a rotationally fixed manner, particularly by means of a keyway. The advantage of this is that the brake motor formed by the electric motor with the brake assembly offers increased operational reliability.

[0041] Further advantages emerge from the dependent claims. The invention is not limited to the combination of features in the claims. Further possible combinations of claims and / or individual claim features and / or features of the description and / or the figures will become apparent to those skilled in the art, particularly from the problem and / or the problem posed by comparison with the prior art.

[0042] The invention will now be explained in more detail using schematic illustrations:

[0043] Figure 1 shows a top view of an annular spring of a brake arrangement according to the invention, in particular of an electric motor, with an inscribed inner circle and outer circle.

[0044] Figure 2 shows the ring spring 1 in plan view.

[0045] Figure 3 shows a brake pad carrier of the brake assembly in a sectional view.

[0046] Figure 4 shows an enlarged section of Figure 3.

[0047] Figure 5 shows an oblique view of a driver 50 of the brake arrangement, onto which the brake pad carrier including the annular spring 1 is pushed.

[0048] Figure 6 shows a front view of the brake pad carrier with the mounted annular spring. The annular spring extends into an inner groove located axially in front of the internal toothing. When the driver 50 is subsequently inserted into the brake pad carrier, i.e., when the brake pad carrier is placed onto the driver 50, the annular spring 1 is elastically deformed, in particular expanded, so that the annular spring 1 then presses against the tooth tips of the external toothing of the driver 50.

[0049] As shown in the figures, the brake arrangement has a ring-like driver 50 which can be plugged onto a shaft, in particular the rotor shaft of the electric motor, and which has an external toothing.

[0050] The driver 50 has a chamfer on its axial end region facing the lining carrier before being inserted into the lining carrier, so that the annular spring 1 received in an inner groove of the lining carrier running circumferentially is widened and rests with a plurality of support points 3 on respective tooth tips of the toothing, in particular external toothing.

[0051] In the area covered by the chamfer in the axial direction, in particular parallel to the axis of rotation of the shaft and / or the driver 50, the outer diameter, in particular the largest outer diameter in the circumferential direction, increases monotonically, in particular strictly monotonically, with increasing distance from the end face of the driver 50 delimiting the chamfer. In the area of ​​the external toothing, in particular axially spaced from the chamfer, the largest outer diameter remains constant regardless of the axial position.

[0052] The support points 3 lie on the inner circle, which has an inner radius R1, i.e. a radial distance R1 to the axis of rotation of the shaft.

[0053] The annular spring 1 presses against the groove base of the inner groove of the lining carrier at support points 2, which lie on the outer circumference of the annular spring 1, which has a radial distance R2 from the rotational axis of the shaft. In particular, the second radial distance R2 is thus greater than the first radial distance R1. The radial distance area covered by the annular spring 1 is located in the axial area covered by the annular spring between the lining carrier and the driver.

[0054] The annular spring 1 is made of a flexible wire that is regularly bent and shaped into a polygonal shape. The flexible wire is made of spring steel.

[0055] The annular spring 1 is interrupted at one point along its circumference and is preferably shaped with odd numbers, in particular heptagonally. The interruption allows for improved elastic deformation, simple production as a bent wire part, and good assembly.

[0056] The annular spring 1 thus has straight sides of the polygon, each of which rests tangentially against the external toothing of the driver 50. The respective support point 3 is located centrally on each side.

[0057] The respective support points 2 are arranged in the corner areas, which connect two nearest adjacent sides of the polygon.

[0058] Support plates 31 are fastened to the base ring 1 of the pad carrier by means of screws 34. For this purpose, the screws 34 are screwed into respective axially directed threaded holes in the base ring 1, so that the screw heads of the screws 34 press the support plates 31 against a step of the base ring 39. The preferably two support plates 31 are pressed against one another and have a respective brake pad 32 on their side facing away from the other support plate 31. The brake pads 32 are arranged radially outside the base ring 1 and border the base ring 1 radially inward. The radial distance area covered by the support plates 31 overlaps with the radial distance area covered by the brake pads 32 and with the radial distance area covered by the base ring 30.

[0059] Due to the elastic tension of the annular spring 1, the driver 50 is held centrally in the internal toothing of the lining carrier.

[0060] The external teeth of the base ring 30 mesh with the internal teeth, with both teeth being designed without a helix angle. Thus, the lining carrier is non-rotatably connected to the driver 50, which in turn is non-rotatably connected, in particular by means of a keyway, to the shaft, in particular the rotor shaft.

[0061] The brake assembly comprises a magnetic body in which an electrically energizable toroidal winding is housed, with the toroidal axis of the toroidal winding aligned coaxially with the rotational axis of the shaft. A ferromagnetic armature disk arranged axially between the toroidal winding and the brake lining carrier is rotationally fixedly connected to the magnetic body and arranged for axial movement relative to the magnetic body.

[0062] The shaft is mounted so that it can rotate relative to the magnet body.

[0063] Preferably, bolts fixed in the magnet body protrude axially through recesses in the armature disk.

[0064] Spring elements supported on the magnet body press on the armature disc.

[0065] When the ring winding is not energized, the armature disk is pressed by the spring elements towards the lining carrier, so that this lining carrier is pressed on its side facing away from the armature disk onto a braking surface which is formed on a friction plate or on a bearing plate of the electric motor, in particular which accommodates a bearing of the shaft.

[0066] A second braking surface is effective when the brake pad carrier and armature plate come into contact. Thus, when the brake is activated, the brake pad carrier is in axial frictional contact on both sides. When the toroidal winding is energized, the armature plate is pulled toward the magnet body against the spring force generated by the spring elements, thus providing axial play for the brake pad carrier.

[0067] According to the invention, the lining carrier is reset from the braking surface facing away from the armature plate by means of the annular spring 1. For this purpose, the annular spring 1 is fixed, in particular axially, at the support points 2 on the brake lining carrier and at the support points 3 on the driver 50. In particular, this means that even with axial back and forth movement of the lining carrier, the annular spring 1 does not shift at the respective support point 2 to the lining carrier and at the respective support point 3 to the driver 50. Thus, even with axial back and forth movement of the lining carrier, the annular spring 1 remains held radially inward and outward by the annular spring 1 by means of static friction, i.e. not sliding friction. Axial slippage is thus prevented.

[0068] Preferably, the return travel when resetting the pad carrier is so large that the pad carrier is centered between the two braking surfaces.

[0069] The inner groove in the base ring 30 is V-shaped. Thus, during the axial reciprocating movement of the lining carrier, a small degree of rotational freedom, in particular a degree of tilting freedom, is provided for the annular spring 1.

[0070] On the other hand, with a rectangular inner groove instead of the V-shaped inner groove, there would essentially be no degree of rotational freedom for the annular spring 1, because the stepped wall of the base ring 30 which axially borders the internal toothing of the brake pad would press flatly onto the annular spring 1 and thus no significant movement of the annular spring 1 would be possible.

[0071] However, by means of the degree of rotational freedom for the annular spring 1 created by the V-shaped inner groove or at least an inclined groove wall, an elastic return of the lining carrier from the braking surface facing away from the armature disk is possible.

[0072] The annular spring 1 is constructed of spring steel wire, the hardness of which is greater than the hardness of the material of the driver 50, in particular, which is steel. The wire diameter of the annular spring 1 is preferably between one percent and two percent of the largest outer diameter of the annular spring 1.

[0073] The tangential contact of the annular spring 1 with the external toothing of the driver 50 at the support points 3 results in the greatest possible lever distance to the support points 2 and thus a greater, more elastic deformation.

[0074] Preferably, each side of the regularly polygonal annular spring 1 touches only a single tooth tip of the external toothing of the driver 50.

[0075] The groove base of the inner groove is wider in the circumferential direction than the diameter of the wire diameter and / or the wire cross-section of the annular spring.

[0076] In further embodiments according to the invention, the inner groove is arranged on the driver 50 so that the annular spring is supported on the groove base of this inner groove and each side of the polygonal annular spring presses on a particularly single tooth tip of the internal toothing of the lining carrier.

[0077] List of reference symbols

[0078] 1 ring spring

[0079] 2 Support point 3 Support point

[0080] 30 base ring

[0081] 31 Supporting plate

[0082] 32 brake pad

[0083] 33 Internal gearing 34 Screw

[0084] 50 Drivers, especially ring-shaped drivers

[0085] R1 inner radius

[0086] R2 outer radius

Claims

Patent claims:

1. Brake arrangement, in particular of an electric motor, wherein the brake arrangement has an annular driver and a lining carrier, wherein the lining carrier has an internal toothing which is placed on an external toothing of the driver, in particular such that the lining carrier is connected to the driver in a rotationally fixed manner and is arranged to be movable axially, in particular parallel to the direction of the ring axis of the driver, relative to the driver, characterized in that the brake arrangement has an annular spring arranged between the driver and the lining carrier, in particular an annular spring arranged between the driver and the lining carrier and extending in the circumferential direction, wherein the annular spring is supported in a groove, in particular wherein the annular spring is supported on the groove base of a groove, wherein the annular spring rests on tooth tips of one of the two toothings, in particular on tooth tips of the internal toothing or the external toothing.

2. Brake arrangement according to claim 1, characterized in that the annular spring is polygonal, in particular regularly polygonal, and / or that the annular spring is formed from a wire, in particular round wire and / or flexible wire, with a polygonal bent shape.

3. Brake arrangement according to one of the preceding claims, characterized in that the annular spring is made from a round wire and / or that the annular spring is made from spring steel.

4. Brake arrangement according to one of the preceding claims, characterized in that the groove is designed as an internal groove in the lining carrier, in particular in a base ring of the lining carrier, and the annular spring rests on tooth tips of the external toothing, in particular wherein the groove is arranged in the axial direction in front of or behind the internal toothing of the lining carrier and the area covered by the external toothing in the axial direction comprises the area covered by the groove in the axial direction, or that the groove is designed as an external groove in the driver and the annular spring rests on tooth tips of the internal toothing, in particular wherein the groove is designed within the external toothing, in particular wherein the area covered by the groove in the axial direction is encompassed by the area covered by the external toothing in the axial direction, in particular wherein the area covered by the internal toothing in the axial direction comprises the area covered by the groove in the axial direction.

5. Brake arrangement according to one of the preceding claims, characterized in that the groove is V-shaped or at least has an inclined groove wall, in particular so that the annular spring executes a rotary movement upon axial movement of the lining carrier relative to the driver, wherein the pivot point of the rotary movement is arranged at the groove base of the groove and the wire thickness and / or the diameter of the wire, in particular round wire, from which the annular spring is made, is smaller than the groove width of the groove at the groove base of the groove, in particular wherein the annular spring rests against the inclined groove wall or against the groove wall of the V-shaped groove at maximum rotational deflection of the annular spring, in particular rests against it in a line.

6. Brake arrangement according to one of the preceding claims, characterized in that one or two support plates are fastened to the base ring, to which brake pads are fastened, in particular to which brake pads are materially connected, in particular wherein the brake pads are spaced from one another in the circumferential direction, in particular regularly.

7. Brake arrangement according to one of the preceding claims, characterized in that the brake pads are arranged radially outside the base ring, and / or that the support plates are fastened by means of axially directed screws which are inserted into axially directed Threaded holes of the base ring are screwed in, are detachably connected to the base ring, in particular wherein the support plates are pressed by the screw heads of the screws towards a collar region of the base part which is formed on the base part, projects radially on the base part and is continuously formed in the circumferential direction.

8. Brake arrangement according to one of the preceding claims, characterized in that the annular spring has an interruption at one point on the circumference and / or that the area covered by the annular spring in the circumferential direction is smaller than 360°, and / or that the annular spring is arranged radially between the driver and the lining carrier, in particular the base ring, in the area covered by the annular spring in the axial direction.

9. Brake arrangement according to one of the preceding claims, characterized in that the number of corners of the polygon is odd, in particular seven.

10. Brake arrangement according to one of the preceding claims, characterized in that the driver has a chamfer on its axial end region facing the lining carrier, in particular the base ring, before being inserted into the lining carrier, in particular the base ring, so that the annular spring received in the circumferentially extending groove is widened, in particular pre-tensioned, and in particular rests with several support points on respective tooth tips of the toothing when the driver is inserted into the lining carrier, in particular the base ring.

11. Brake arrangement according to one of the preceding claims, characterized in that in the area covered by the chamfer in the axial direction, in particular thus parallel to the axis of rotation of the shaft and / or the driver, the outer diameter of the driver increases monotonically, in particular strictly monotonically, with increasing distance from the end face of the driver delimiting the chamfer, in particular wherein in the area from the external toothing in the axial direction, in particular axially spaced from the chamfer, the largest outer diameter is independent of the axial position.

12. Brake arrangement according to one of the preceding claims, characterized in that the brake arrangement has a magnetic body in which an electrically energizable ring winding is accommodated, wherein the ring axis of the ring winding is aligned coaxially with the axis of rotation of the shaft, wherein a ferromagnetic armature disk arranged axially between the ring winding and the lining carrier is connected to the magnetic body in a rotationally fixed manner and is arranged to be axially movable relative to the magnetic body, wherein the shaft is arranged to be rotatably mounted relative to the magnetic body, in particular wherein bolts fastened in the magnetic body project axially through recesses in the armature disk, wherein spring elements supported on the magnetic body press on the armature disk, in particular wherein the brake arrangement is designed such that when the ring winding is not energized, the armature disk is pressed towards the lining carrier by the spring elements,so that this lining carrier is pressed on its side facing away from the armature disk onto a braking surface which is formed on a friction plate or on a bearing plate of the electric motor, in particular which accommodates a bearing of the shaft, in particular wherein the braking arrangement is designed such that when the annular winding is energized, the armature disk is drawn towards the magnetic body against the spring force generated by the spring elements and thus axial play is provided to the lining carrier, so that a restoring force generated by the elastically deformed annular spring retracts the lining carrier axially, in particular in the axial direction, from the braking surface facing away from the armature disk.

13. Brake arrangement according to one of the preceding claims, characterized in that when the toothing is designed as external toothing, the straight sides of the polygonally shaped annular spring each bear tangentially against the external toothing of the driver, in particular wherein a respective support point is arranged centrally in each of the sides and the corner regions of the polygonally shaped annular spring have the respective support points at which the annular spring is supported on the groove base of the groove, in particular wherein the corner regions each connect two of those sides of the polygon which are closest to one another.

14. Brake arrangement according to one of the preceding claims, characterized in that when the groove is designed as an inner groove, the support points are arranged on the inscribed inner circle of the polygon and / or that when the groove is designed as an outer groove, the support points are arranged on the circumscribed outer circle of the polygon.

15. Electric motor with a brake arrangement according to one of the preceding claims, characterized in that the driver is placed on a rotor shaft of the electric motor and is connected in a rotationally fixed manner to the rotor shaft, in particular by means of a key connection.

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