Brake device and electric machine having brake device

Abstract

The invention relates to a brake device, in particular for an electric machine, said brake device having an annular driver and a brake pad carrier, said brake pad carrier having an internal toothing which is fitted onto an external toothing of the driver, said brake device having an annular spring which is arranged between the driver and the brake pad carrier, the annular spring is supported in the groove, and the annular spring abuts against the tooth top of one of the two tooth portions.

Description

Technical Field

[0001] The present invention relates to a braking device and an electric motor having a braking device. Background Art

[0002] As is well known, a braking device includes a brake pad carrier having brake pads.

[0003] As the latest prior art, a shaft-hub connection is known from DE 10 2022 001 345 A1.

[0004] A toothed clutch with spring cushioning is known from DE 10 2011 121 790 A1.

[0005] An alignment device for a gear transmission is known from DE 78 25 113 U1.

[0006] A spring brake with a brake disc is known from DE 10 2006 010 656 B3, the brake disc having friction surfaces on opposite sides.

[0007] A shaft-hub connection having locking hooks radially outwardly directed on a spring plate is known from DE 10 2017 104 598 A1. Summary of the Invention

[0008] Therefore, the object of the present invention is to enable the safe operation of the braking device and the electric motor including the braking device.

[0009] According to the present invention, this object is achieved by a braking device with the features given in claim 1 and an electric motor with the features given in claim 15.

[0010] In the braking device, especially the braking device of an electric motor, an important feature of the present invention is that the braking device has an annular driving member and a brake pad carrier,

[0011] wherein the brake pad carrier has an internal tooth portion which is sleeved on the external tooth portion of the driving member, especially the brake pad carrier is non-rotatably connected to the driving member and is arranged to be movable relative to the driving member axially, i.e., especially in a direction parallel to the ring axis of the driving member.

[0012] wherein the braking device has an annular spring, especially an annular spring extending circumferentially, arranged between the driving member and the brake pad carrier,

[0013] wherein the annular spring is supported in a groove, especially on the bottom of the groove,

[0014] The annular spring is rested on the tooth top of one of the two tooth parts, especially on the tooth top of the inner tooth part or the outer tooth part.

[0015] The advantage here is that the safe operation of the braking device can be achieved. In particular, the safe disconnection / separation of the brake can be ensured, because when the brake is engaged, the annular spring is elastically deflected in the axial direction by the brake pad carrier, and then when the brake is disconnected, the annular spring causes or at least assists the reset of the brake pad carrier. That is, in particular, the elastically deflected and relaxed annular spring at disconnection assists the brake pad carrier to lift off from the braking surface.

[0016] This behavior of the annular spring is achieved in such a way that the annular spring is supported radially in the groove on the one hand, and thus axially limited, and on the other hand, it is rested on the tooth top in a firmly pressed manner in the radial direction, so that the annular spring does not slide axially on the corresponding tooth top, but is held on the tooth top sufficiently firmly by means of static friction. In this way, when the braking device is engaged, i.e., especially activated, it is reliably ensured that the annular spring deflects elastically, and this elastic deflection is eliminated when the brake is disconnected, so that the brake pad carrier with its brake pads facing the braking surface is pulled away from the braking surface, especially by means of the relaxation of the annular spring.

[0017] In an advantageous design, the annular spring is formed as a polygon, especially a regular polygon. The advantage here is that well-defined support points and resting points are provided. In particular, the corresponding points are spaced apart from each other circumferentially, especially regularly.

[0018] Through this spacing, a lever arm is provided between the corresponding support point and the two resting points respectively adjacent to the support point, and this lever arm ensures a well-defined reset force for pulling the brake pad carrier away from the braking surface.

[0019] The circumferential direction, the radial direction and the axial direction are respectively based on the driving member, the brake pad carrier and / or the axis that is non-rotatably connected to the driving member, especially the rotation axis of the rotor shaft of the motor.

[0020] In an advantageous design, the annular spring is formed as a polygon from metal wire, especially round wire and / or bent metal wire. The advantage here is that simple manufacturing can be achieved.

[0021] In an advantageous design, the annular spring is made of round wire. The advantage here is that the annular spring can be simply made into a bent part.

[0022] In an advantageous design, the annular spring is made of spring steel. The advantage here is that the annular spring has a sufficiently large elastic deflection range so that it does not undergo inelastic deformation within the working range. The working range includes the deflection that occurs between the disengaged state and the engaged state of the brake block carrier in the braking device.

[0023] In an advantageous design, the groove is implemented as an internal groove in the brake block carrier, in particular as an internal groove in the base ring of the brake block carrier, and the annular spring bears on the tooth tips of the external teeth.

[0024] In particular, the groove is arranged axially in front of or behind the internal teeth of the brake block carrier, and the region covered by the external teeth in the axial direction includes the region covered by the groove in the axial direction. The advantage here is that the annular spring is supported radially outside the bearing point on the tooth tips. Therefore, compared to bearing force-locking on the tooth tips, the form-locking reception in the groove is achieved at a greater radial distance. In addition, the manufacture of the groove can be implemented very simply because the groove is not implemented within the teeth but axially beside the teeth.

[0025] In an alternative advantageous design, the groove is implemented as an external groove in the drive member, and the annular spring bears on the tooth tips of the internal teeth.

[0026] In particular, the groove is implemented within the external teeth. In particular, the region covered by the external teeth in the axial direction includes the region covered by the groove in the axial direction.

[0027] In particular, the region covered by the internal teeth in the axial direction includes the region covered by the groove in the axial direction. The advantage here is that although the groove has to be provided within the teeth, the teeth of the teeth help to axially limit the annular spring. At this time, support is carried out radially inside the bearing position on the tooth tips of the internal teeth.

[0028] In an advantageous design, the groove is implemented as V-shaped or has at least one inclined groove wall.

[0029] In particular, so that the annular spring rotates when the brake block carrier moves axially relative to the drive member, wherein the rotation point / pivot point of the rotation is arranged on the bottom of the groove, and the wire thickness and / or diameter of the metal wire, in particular round wire, forming the annular spring is less than the groove width at the bottom of the groove.

[0030] In particular, when the annular spring is deflected to the maximum extent, the annular spring abuts against the inclined groove wall or the groove wall of the V-shaped groove, in particular linearly abuts against the inclined groove wall or the groove wall of the V-shaped groove.

[0031] The advantage here is that the angled groove walls increase the rotational freedom, in particular the tilting freedom, of the annular spring. Thus, compared to straight groove walls, a greater range of rotation can be achieved for the annular spring supported on the groove bottom when the brake pad carrier moves axially.

[0032] To receive the annular spring, the groove is wider than the wire thickness of the round wire from which the annular spring is made. That is, in particular, the diameter of the round wire is smaller than the groove width, i.e., in particular smaller than the groove width measured at the groove bottom of the groove.

[0033] Thus, the angled groove walls can achieve a greater range of rotation for the annular spring, where the pivot point is arranged on the groove bottom.

[0034] In an advantageous design, one or two carrier plates are fastened to the base ring, and the brake pads are fastened to the carrier plates. In particular, the brake pads are connected to the carrier plates in a material-locking manner.

[0035] In particular, the brake pads are spaced apart from one another circumferentially, in particular evenly. The advantage here is that the brake pads are fastened to one side of respective separate plates, so that brake pads are fastened on both axial sides of the brake pad carrier in total. Simple manufacture can be achieved, since the two separate plates are placed as a stack onto the radially protruding and circumferentially surrounding flange region of the base ring and are fastened by means of screws screwed axially into the flange region. Here, the brake pads are mounted on the separate plates and are arranged radially outside the base ring, in particular outside the flange region. In this way, the brake pads are protected from strong forces.

[0036] In an advantageous design, the brake pads are arranged radially outside the base ring. The advantage here is that the brake pads are mechanically protected, in particular from the fastening forces introduced by the screws. Preferably, the brake pads are connected to the separate plates in a material-locking manner, in particular by bonding. Thus, the brake pads only have to transmit the frictional torque generated when the brake device is engaged, i.e., in particular activated, and are not subject to any other forces. Since the separate plates are more elastic than the base ring, the manufacturing tolerances are eliminated or at least sufficiently compensated for by the elastic deformation of the separate plates.

[0037] In an advantageous design, the carrier plate is detachably connected to the base ring by means of axially directed screws, which are screwed into axially directed threaded holes in the base ring.

[0038] In particular, the carrier plate is pressed against the flange region of the base part by the screw heads of the screws, which flange region is formed on the base part, radially protrudes on the base part and is constructed without interruption circumferentially. The advantage here is that the separate plates are pushed onto the base ring as an axially directed stack from the axial direction, and the stack is pressed against the flange region by one or more screws, in particular regularly spaced from one another circumferentially.

[0039] In an advantageous design, the annular spring has an interruption at a location on the circumference. The advantage here is that higher elasticity can be achieved, and it is possible to simply produce a bent wire piece, and in particular, simple installation can be achieved by unfolding the leg region, especially simple installation on the drive member.

[0040] In an advantageous design, the range covered by the annular spring in the circumferential direction is less than 360°. The advantage here is that the annular spring is implemented to be interrupted at a location in the circumferential direction, and thus higher elasticity can be achieved.

[0041] In an advantageous design, in the region covered by the annular spring in the axial direction, the annular spring is arranged radially between the drive member and the brake pad carrier, especially the base ring. The advantage here is that the brake pad carrier is centered relative to the drive member, thereby reducing noise emissions during operation, especially during shaft rotation. In particular, rattling noises caused by relative vibrations oriented circumferentially or radially can be suppressed. In addition, an axial restoring force can be provided for the brake pad carrier to pull the brake pad carrier back from the brake surface when the braking device is disengaged.

[0042] In an advantageous design, the number of corners of the polygon is odd, especially seven. The advantage here is that vibrations generated in the circumferential direction can be more effectively suppressed because for the fundamental vibration, the harmonics have an even number of nodes, and thus even harmonics are more easily excited. However, the number of corners of the annular spring is odd, so it is less likely to be excited to generate vibrations.

[0043] In an advantageous design, before the drive member is inserted into the brake pad carrier, especially the base ring, the drive member has a chamfer on the axial end region facing the brake pad carrier, so that the annular spring received in the circumferentially surrounding groove is expanded, especially pre-tensioned when the drive member is inserted into the brake pad carrier, especially the base ring.

[0044] And in particular, the annular spring abuts against the respective tooth tops of the tooth part by means of a plurality of abutment points. The advantage here is that when inserted in an axially directed manner, the annular spring is pre-tensioned, and thus is arranged between the drive member and the brake pad carrier in a fully anti-slip fixed manner.

[0045] In an advantageous design, in the region covered by the chamfer in the axial direction, that is, especially in the direction parallel to the axis and / or the rotation axis of the drive member, the outer diameter of the drive member increases monotonically, especially strictly monotonically, as the distance from the end side defining the chamfer of the drive member increases.

[0046] In particular, in the region covered by the external tooth portion in the axial direction, that is, in the region axially spaced from the chamfer, the corresponding maximum outer diameter is independent of the axial position. The advantage here is that when inserted in an axially directed manner, the annular spring is pre-tensioned and is thus arranged between the driving member and the brake pad carrier in a fully anti-slip fixed manner.

[0047] In an advantageous design, the braking device has a magnet in which an energizable annular winding is received.

[0048] The axis of the annular winding is coaxial with the axis of rotation of the shaft.

[0049] An axially arranged ferromagnetic armature plate between the annular winding and the brake pad carrier is non-rotatably connected to the magnet and is arranged to be axially movable relative to the magnet.

[0050] The shaft is supported so as to be rotatable relative to the magnet.

[0051] In particular, a bolt fixed in the magnet axially passes through the notch of the armature plate.

[0052] A spring element supported on the magnet presses against the armature plate.

[0053] In particular, the braking device is designed such that when the annular winding is not energized, the armature plate is pressed by the spring element towards the brake pad carrier, so that the brake pad carrier is pressed against the braking surface on the side facing away from the armature plate. The braking surface is formed on the friction plate or formed at the bearing cover of the motor, in particular the bearing cover that houses the bearing of the shaft.

[0054] In particular, the braking device is designed such that when the annular winding is energized, the armature plate is attracted towards the magnet against the spring force generated by the spring element, and thus an axial clearance is provided for the brake pad carrier, so that the restoring force generated by the elastically deformed annular spring axially pulls the brake pad carrier back from the braking surface, especially in the axial direction. The advantage here is that in the case of current interruption, engagement occurs automatically and thus higher operating safety can be achieved, especially the operating safety of the drive device protected by the braking device.

[0055] When the brake pad carrier contacts the armature plate, the second braking surface comes into play. That is, when the brake is activated, the brake pad carrier is in frictional contact on both sides axially.

[0056] In an advantageous design, in the case where the tooth portion is implemented as an external tooth portion, the straight edges of the annular spring formed as a polygon are respectively in tangential contact with the external tooth portion of the driving member.

[0057] In particular, corresponding resting points are arranged at the midpoints of each side, and the corner regions of the annular spring formed as a polygon have corresponding support points, where the annular spring is supported on the bottom of the groove at these support points. In particular, the corner regions connect every two adjacent sides of the polygon respectively. The advantage here is that a large lever arm can be achieved between the resting points on the corresponding tooth tops and the associated support points. Therefore, the annular spring can be firmly pressed against the driving member and the brake block carrier.

[0058] In an advantageous design, when the groove is implemented as an internal groove, the resting points are arranged on the inscribed circle of the polygon. The advantage here is that the resting points are thus arranged at the centers of the respective sides, and thus there is a sufficiently large lever arm relative to the circumferentially adjacent support points respectively, so that when the brake block carrier moves axially towards the brake surface, a sufficiently high elastic preloading force can be achieved to provide a restoring force that acts when the braking device is disengaged.

[0059] In an advantageous design, when the groove is implemented as an external groove, the support points are arranged on the circumscribed circle of the polygon. The advantage here is that there is a sufficiently large lever arm between the resting points and the respective circumferentially adjacent support points respectively, so that when the brake block carrier moves axially towards the brake surface, a sufficiently high elastic preloading force can be achieved to provide a restoring force that acts when the braking device is disengaged.

[0060] In a motor with a braking device, an important feature is that the driving member is sleeved on the rotor shaft of the motor and is connected to the rotor shaft in a non-rotatable manner, in particular by means of a key connection to the rotor shaft. The advantage here is that the braking motor formed by the motor with the braking device has higher operating safety.

[0061] Further advantages are given by the dependent claims. The invention is not limited to the feature combinations of the claims. For a person skilled in the art, in particular for the purposes set and / or by comparison with the prior art, other reasonable combination possibilities of the claims and / or the features of the individual claims and / or the features of the description and / or the features of the drawings can be obtained. Description of the Drawings

[0062] The present invention will now be described in more detail with reference to the schematic drawings:

[0063] Figure 1 The braking device according to the invention, in particular the annular spring of a motor, is shown in a top view with an inscribed circle and a circumscribed circle.

[0064] Figure 2 The annular spring 1 is shown in a top view.

[0065] Figure 3The brake pad carrier of the braking device is shown in a sectional view.

[0066] Figure 4 is shown enlarged Figure 3 of a partial region.

[0067] Figure 5 The driving member 50 of the braking device is shown in an oblique view, onto which the brake pad carrier together with the annular spring 1 is pushed.

[0068] Figure 6 A front view of the brake pad carrier with the installed annular spring is shown, wherein the annular spring projects into an internal groove which is axially arranged in front of the internal tooth portion. When the driving member 50 is later pushed into the brake pad carrier, i.e., when the brake pad carrier is slipped onto the driving member 50, the annular spring 1 is elastically deformed, in particular expanded, such that in particular the annular spring 1 is pressed onto the tooth tips of the external tooth portion of the driving member 50. DETAILED DESCRIPTION

[0069] As shown, the braking device has an annular driving member 50 which can be slipped onto a shaft, in particular the rotor shaft of an electric motor, and the driving member has an external tooth portion.

[0070] Before the driving member 50 is inserted into the brake pad carrier, the driving member has a chamfer in the axial end region facing the brake pad carrier, so as to expand the annular spring 1 which is received in the circumferentially surrounding internal groove of the brake pad carrier, and the annular spring bears against the tooth portion, in particular against the respective tooth tips of the external tooth portion, by means of a plurality of abutment points 3.

[0071] Thus, in the region covered by the chamfer in the axial direction, i.e., in particular in the direction parallel to the shaft and / or the axis of rotation of the driving member 50, the outer diameter, in particular the circumferentially largest outer diameter, increases monotonically, in particular strictly monotonically, as the distance from the end face defining the chamfer of the driving member 50 increases. In the region of the external tooth portion which is axially spaced from the chamfer, in particular, the respective largest outer diameter is independent of the axial position.

[0072] The abutment points 3 are located on an inner circle having an inner radius R1, which is the radial distance R1 of the abutment points from the axis of rotation of the shaft.

[0073] The annular spring 1 is pressed onto the bottom of the internal groove of the brake pad carrier by means of support points 2 which are located on the outer circle of the annular spring 1 and which have a radial distance R2 from the axis of rotation of the shaft. In particular, the second radial distance R2 is thus greater than the first radial distance R1. The radial range covered by the annular spring 1 is arranged in the axial region covered by the annular spring between the brake pad carrier and the driving member.

[0074] The annular spring 1 is made of a bent metal wire, and the bent metal wire is regularly bent and formed into a polygon. The bent metal wire is made of spring steel.

[0075] The annular spring 1 is interrupted at a part of its circumference and is preferably formed into an odd-sided polygon, especially a heptagon. Through this interruption, an improvement in elastic deformation, a simple formation of the metal wire bending part, and good mountability can be achieved.

[0076] Therefore, the annular spring 1 has straight sides of a polygon, and these straight sides respectively abut against the outer teeth of the driving part 50 in a tangential manner. Corresponding abutting points 3 are arranged in each side.

[0077] In the corner regions where every two adjacent sides of the polygon are respectively connected, corresponding support points 2 are arranged.

[0078] The bearing plate 31 is fastened to the base ring 1 of the brake block carrier by means of screws 34. For this purpose, the screws 34 are screwed into the corresponding axially directed threaded holes of the base ring 1, so that the screw heads of the screws 34 press the bearing plate 31 against the step of the base ring 39. Preferably, the two bearing plates 31 press against each other and have corresponding brake block carriers 32 on the sides facing away from the other bearing plate 31 respectively.

[0079] The brake block carrier 32 is arranged radially outside the base ring 1 and is adjacent to the base ring 1 radially inward. The radial range covered by the bearing plate 31 overlaps with the radial range covered by the brake block carrier 32 and also overlaps with the radial distance region covered by the base ring 30.

[0080] By the elastic clamping of the annular spring 1, the driving part 50 is centered in the inner teeth of the brake block carrier.

[0081] The outer teeth of the base ring 30 engage into the inner teeth, and the two tooth parts are implemented without a helix angle. Therefore, the brake block carrier is connected to the driving part 50 in a non-rotatable manner, and the driving part is in turn connected to the shaft, especially the rotor shaft, in a non-rotatable manner, especially by means of a key connection.

[0082] The braking device has a magnet in which an energizable annular winding is received, and the ring axis of the annular winding is oriented coaxially with the rotational axis of the shaft. The ferromagnetic armature plate axially arranged between the annular winding and the brake block carrier is connected to the magnet in a non-rotatable manner and is arranged to be axially movable relative to the magnet.

[0083] The shaft is supported in a rotatable manner relative to the magnet.

[0084] Preferably, the bolts fastened in the magnet axially pass through the notches of the armature plate.

[0085] The spring element supported at the magnet presses against the armature plate.

[0086] In the case where the annular winding is not energized, the armature plate is pressed against the brake block carrier by the spring element, so that the brake block carrier is pressed against the braking surface on the side facing away from the armature plate, and the braking surface is formed on the friction plate or on the bearing cover of the motor. In particular, the bearing cover receives the bearing of the shaft.

[0087] When the brake block carrier comes into contact with the armature plate, the second braking surface comes into play. That is, when the brake is activated, both axially sides of the brake block carrier are in frictional contact.

[0088] When the annular winding is energized, the armature plate is attracted towards the magnet against the spring force generated by the spring element, and thus an axial clearance is provided for the brake block carrier.

[0089] According to the invention, the return of the brake block carrier from the braking surface facing away from the armature plate is achieved by means of the annular spring 1. For this purpose, the annular spring 1 is fixed to the brake block carrier axially through the support point 2 and to the driving member 50 through the abutment point 3. This especially means that even if the brake block carrier moves axially back and forth, the annular spring 1 neither moves relative to the brake block carrier at the corresponding support point 2 nor moves relative to the driving member 50 at the corresponding abutment point 3. That is, even if the brake block carrier moves axially back and forth, from the perspective of the annular spring 1, the annular spring 1 is held both radially inwards and outwards by static friction (i.e., not sliding friction). Therefore, axial sliding is prevented.

[0090] Preferably, the return stroke when the brake block carrier returns is designed such that the brake block carrier is centered between the two braking surfaces.

[0091] The inner groove in the base ring 30 is V-shaped. Therefore, when the brake block carrier moves axially back and forth, a relatively small degree of rotational freedom, especially tilting freedom, is provided for the annular spring 1.

[0092] On the contrary, in the case where the inner groove is rectangular instead of V-shaped, the annular spring 1 basically has no rotational freedom because the stepped wall surface of the base ring 30 axially adjacent to the inner tooth portion of the brake block presses against the annular spring 1, and thus the annular spring 1 cannot move significantly.

[0093] However, by means of the rotational freedom created for the annular spring 1 through the V-shaped inner groove or at least one inclined groove wall, the elastic return of the brake block carrier from the braking surface facing away from the armature plate can be achieved.

[0094] The annular spring 1 is implemented as a spring wire, and its hardness is greater than the hardness of the material of the driving member 50. In particular, the material of the driving member is steel.

[0095] Preferably, the wire diameter of the annular spring 1 is between 1% and 2% of the maximum outer diameter of the annular spring 1.

[0096] By the annular spring 1 contacting tangentially with the outer tooth portion of the driving member 50 at the abutment point 3, a force arm distance as large as possible from the support point 2 is achieved, and thus a larger elastic deformation is achieved.

[0097] Preferably, each side of the annular spring 1 configured as a regular polygon only contacts the sole tooth top of the outer tooth portion of the driving member 50.

[0098] The circumferential width of the bottom of the inner groove is larger than the wire diameter of the annular spring and / or the diameter of the wire cross-section.

[0099] In a further embodiment according to the invention, the inner groove is arranged at the driving member 50, such that the annular spring is supported at the bottom of the inner groove, and each side of the polygonal annular spring presses onto in particular the sole tooth top of the inner tooth portion of the brake block carrier.

[0100] List of reference signs:

[0101] 1 Annular spring

[0102] 2 Support point

[0103] 3 Abutment point

[0104] 30 Base ring

[0105] 31 Carrier plate

[0106] 32 Brake block

[0107] 33 Inner tooth portion

[0108] 34 Screw

[0109] 50 Driving member, in particular an annular driving member

[0110] R1 Inner radius

[0111] R2 Outer radius

Claims

1. A braking device, in particular a braking device for an electric motor, The braking device has an annular drive element and a brake block carrier, The brake block carrier has an internal tooth part, which is sleeved on the external tooth part of the drive element, in particular so that the brake block carrier is connected to the drive element in a non-rotatable manner and is arranged to be movable relative to the drive element axially, that is, in particular in a direction parallel to the ring axis of the drive element, It is characterized in that, The braking device has an annular spring arranged between the drive element and the brake block carrier, in particular an annular spring extending circumferentially between the drive element and the brake block carrier, The annular spring is supported in a groove, in particular, the annular spring is supported on the bottom of the groove, The annular spring abuts against the top of one of the two tooth parts, in particular the top of the internal tooth part or the external tooth part.

2. The braking device according to claim 1, characterized in that, The annular spring is formed into a polygon, in particular a regular polygon, and / or The annular spring is formed into a polygon from a metal wire, in particular a round wire and / or a bent metal wire.

3. The braking device according to any one of the above claims, characterized in that, The annular spring is made of a round wire, and / or The annular spring is made of spring steel.

4. The braking device according to any one of the above claims, characterized in that, The groove is implemented as an internal groove in the brake block carrier, in particular an internal groove in the base ring of the brake block carrier, and the annular spring abuts against the top of the external tooth part, In particular, the groove is arranged axially in front of or behind the internal tooth part of the brake block carrier, and the region covered by the external tooth part in the axial direction includes the region covered by the groove in the axial direction, Or, The groove is implemented as an external groove in the drive element, and the annular spring abuts against the top of the internal tooth part, In particular, the groove is implemented within the external tooth part, in particular, the region covered by the external tooth part in the axial direction includes the region covered by the groove in the axial direction, In particular, the region covered by the internal tooth part in the axial direction includes the region covered by the groove in the axial direction.

5. The braking device according to any one of the above claims, characterized in that, The groove is implemented as V-shaped or has at least one inclined groove wall, In particular, so that the annular spring performs a rotational movement when the brake block carrier moves axially relative to the drive element, wherein the rotation point of the rotation is arranged on the bottom of the groove, and the wire thickness and / or diameter of the metal wire, in particular the round wire, forming the annular spring is smaller than the groove width at the bottom of the groove, In particular, when the annular spring is deflected to the maximum extent, the annular spring abuts against the inclined groove wall or the groove wall of the V-shaped groove, in particular linearly abuts against the inclined groove wall or the groove wall of the V-shaped groove.

6. The braking device according to any one of the above claims, characterized in that, One or two carrier plates are fastened to the base ring, and the brake blocks are fastened at the carrier plates. In particular, the brake blocks are connected to the carrier plates by material locking, In particular, the brake blocks are circumferentially spaced apart from each other, in particular regularly spaced apart.

7. The braking device according to any one of the above claims, characterized in that, The brake blocks are arranged radially outside the base ring, and / or, The bearing plate is detachably connected to the base ring by means of axially directed screws which are screwed into axially directed threaded holes of the base ring. In particular, the bearing plate is pressed by the screw heads of the screws against a flange region formed on the base part of the base part, which flange region projects radially at the base part and is configured discontinuously in the circumferential direction.

8. The braking device according to any one of the preceding claims, characterized in that the annular spring has an interruption at a portion of the circumference, and / or the range covered by the annular spring in the circumferential direction is less than 360°, and / or the annular spring is arranged radially between the driving member and the brake block carrier, in particular the base ring, in the region covered by the annular spring in the axial direction.

9. The braking device according to any one of the above claims, characterized in that, The number of corners of the polygon is odd, in particular seven.

10. The braking device according to any one of the preceding claims, characterized in that before the driving member is inserted into the brake block carrier, in particular into the base ring, the driving member has a chamfer on the axially facing end region facing the brake block carrier, so that the annular spring received in the circumferentially surrounding groove is expanded, in particular pre-tensioned, when the driving member is inserted into the brake block carrier, in particular into the base ring. In particular, the annular spring abuts against the respective tooth tops of the tooth part by means of a plurality of abutment points.

11. The braking device according to any one of the preceding claims, characterized in that in the region covered by the chamfer in the axial direction, that is, in particular in the direction parallel to the axis and / or the rotational axis of the driving member, the outer diameter of the driving member increases monotonically, in particular strictly monotonically, as the distance from the end side defining the chamfer of the driving member increases. In particular, in the region covered by the external tooth part in the axial direction, that is, in particular axially spaced from the chamfer, the respective maximum outer diameter is independent of the axial position.

12. The braking device according to any one of the preceding claims, characterized in that the braking device has a magnet in which an energizable annular winding is received. The ring axis of the annular winding is coaxial with the rotational axis of the shaft. The ferromagnetic armature plate axially arranged between the annular winding and the brake block carrier is non-rotatably connected to the magnet and is arranged to be axially movable relative to the magnet. The shaft is arranged to be supported so as to be rotatable relative to the magnet. In particular, the bolt fixed in the magnet axially passes through the notch of the armature plate. The spring element supported at the magnet presses against the armature plate. In particular, the braking device is designed such that when the annular winding is not energized, the armature plate is pressed by the spring element against the brake block carrier, so that the brake block carrier is pressed against the braking surface on the side facing away from the armature plate, which braking surface is formed on the friction plate or on the bearing cover of the electric motor, in particular the bearing cover receives the bearing of the shaft. In particular, the braking device is designed such that when the annular winding is energized, the armature plate is attracted towards the magnet against the spring force generated by the spring element, thus providing an axial clearance for the brake block carrier, so that the restoring force generated by the elastically deformed annular spring axially, in particular in the axial direction, pulls the brake block carrier back from the braking surface facing away from the armature plate.

13. The braking device according to any one of the preceding claims, characterized in that In the case where the tooth part is implemented as an external tooth part, the straight edges of the annular spring formed as a polygon are respectively in tangential contact with the external tooth part of the driving part. In particular, corresponding abutment points are arranged at the center of each side, and the corner regions of the annular spring formed as a polygon have corresponding support points, and the annular spring is supported on the bottom of the groove at these support points. In particular, the corner regions respectively connect every two adjacent sides of the polygon.

14. The braking device according to any one of the above claims, characterized in that, In the case where the groove is implemented as an internal groove, the abutment points are arranged on the inscribed circle of the polygon, and / or In the case where the groove is implemented as an external groove, the support points are arranged on the circumscribed circle of the polygon.

15. A motor, the motor having a braking device according to any one of the preceding claims, characterized in that, The driving part is sleeved on the rotor shaft of the motor and is connected to the rotor shaft in a non-rotatable manner, especially by means of a key connection.

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