Drive device with electric machine provided with a brake assembly

Abstract

The invention relates to a drive device having an electric machine provided with a brake assembly, wherein the electric machine has a housing part and a rotor rotatably supported by a first bearing and a second bearing, wherein the first bearing has an inner ring and an outer ring, wherein the inner ring of the first bearing is received, in particular, is telescopically received, on the rotor and, in particular, is seated against a step or is pressed against a driving element which is seated against a step formed at the rotor, wherein the brake assembly has a magnet, in particular, a magnet made of a ferromagnetic material, wherein the outer ring of the first bearing is received in the magnet of the brake assembly and, in particular, is seated against a step.

Description

Technical Field

[0001] The present invention relates to a drive device having a motor equipped with a braking component. Background Technology

[0002] Drive mechanisms with electric motors are commonly known.

[0003] An electromagnetic brake is known from DE 22 57 290 A.

[0004] An electric motor with redundant brakes is known from DE 10 2012 019 415 A1.

[0005] A brake is known from DE 10 2012 010 790 A1.

[0006] A braking device is known from DE 10 2013 005 239 A1.

[0007] A geared motor is known from WO 2004 / 077 644 A2.

[0008] A motor with an angle sensor is known from DE 10 2008 037 737 A1.

[0009] A device for establishing braking force transmission is known from DE 20 2016 107 420 U1. Summary of the Invention

[0010] Therefore, the objective of this invention is to achieve precise drive control.

[0011] In a drive device having a motor equipped with a braking assembly, an important feature of the present invention is that the motor has a housing and a rotor rotatably supported by a first bearing and a second bearing.

[0012] The first bearing has an inner ring and an outer ring.

[0013] In this configuration, the inner ring of the first bearing is received, particularly fitted onto the rotor, and especially abuts against the stepped portion, or presses against the driving member, which abuts against the stepped portion formed on the rotor.

[0014] The braking assembly includes a magnet / magnetic body, particularly a magnet made of ferromagnetic material.

[0015] The outer ring of the first bearing is received in the magnet of the braking assembly, and in particular abuts against the step portion.

[0016] The advantage at this point is that precise control of the drive unit is achieved. Because of the two fixed bearings on the rotor, stable angle detection with low error is achieved at the rotor of the drive unit, which is configured as a geared motor, wherein the detected angle value is proportional to the output shaft angle value as precisely as possible.

[0017] Therefore, by applying a fixed bearing in the area of ​​the angle sensor, very accurate angle detection can be achieved even when expansion occurs in the drive unit due to heat, because the distance of the first bearing, which is constructed as a fixed bearing, relative to the angle sensor is much smaller than the distance between the first bearing and the second bearing.

[0018] Because the rotor's second bearing, i.e., the bearing on the reducer side, is also a fixed bearing, the helical-toothed sun gear inserted into the rotor shaft remains essentially in its axial position during thermal expansion. Although the distance between the first and second bearings—especially relative to the housing—changes due to thermal length variations, the sun gear does not rotate even with its helical teeth, and the angle sensor operates undisturbed.

[0019] The first bearing is housed within the magnet of the braking assembly. Therefore, the change in distance between the first and second bearings is not compensated for by the movement of the first bearing within the magnet, but rather by the movement of the magnet relative to the receiving element, i.e., relative to the housing element.

[0020] Therefore, in this way, a fixed support with axial bilateral support that has stable angle detection relative to thermal effects is achieved.

[0021] Preferably, the rotor is made of steel, and the housing is made of aluminum. That is, according to the invention, when the rotor and housing are made of different materials, angular errors can be prevented or at least reduced.

[0022] In an advantageous design, the second bearing, particularly its outer ring, is received within the housing or in a flange connected to the housing component, and particularly abuts against a stepped portion. The advantage here is that thermal changes in the length of the housing and / or rotor, particularly the length of the housing relative to the rotor, do not cause torsion of the reducer shaft, even if the reducer shaft is connected to a toothed component with helical teeth in a manner that prevents relative rotation.

[0023] In an advantageous design, the inner ring of the second bearing is received, particularly fitted onto the rotor, and especially abuts against the stepped portion. Advantageously, the second bearing is implemented as a fixed bearing, so the angle value detected at the rotor is proportional to the angle value of the reducer output shaft. This is particularly suitable for toothed components connected to the rotor in a manner that prevents relative rotation, especially when the sun gear is implemented with helical teeth.

[0024] In an advantageous design, the magnet is received in a receiving element fixedly connected to the housing element, or is received within the housing element itself.

[0025] The magnets are arranged to move along the axial direction, specifically parallel to the rotor's axis of rotation, and are connected to the first torque support member, particularly by means of second screws, which are evenly spaced apart from each other in the circumferential direction.

[0026] The first torque support is connected to the receiving member and / or housing member, particularly by means of first screws, which are evenly spaced apart in the circumferential direction. The advantage here is that the magnet can move relative to the receiving member and / or relative to the motor housing member when its length changes due to heat. Nevertheless, the first and second bearings maintain their fixed bearing function.

[0027] In an advantageous design, the first torque support is implemented as a bellows, particularly a metal bellows, wherein the area of ​​the first torque support that contacts the receiver is spaced apart from the area that contacts the magnet in the axial direction, and particularly the area that contacts the magnet is arranged at a smaller radial distance compared to the area of ​​the receiver. The advantage here is that the bearing clamping force is generated by the same component also used as a torque support for the magnet, because the magnet is received in the receiver in a manner that allows it to move not only in the axial direction but also to rotate in the circumferential direction.

[0028] In another advantageous design, the first torque support, particularly the metal plate, is implemented as a plate such that the area of ​​the contact receiver of the first torque support is arranged at the same axial position as the area of ​​the torque support in contact with the magnet, and particularly, the area in contact with the magnet is arranged at a smaller radial distance compared to the area of ​​the contact receiver. The advantage here is that the torque support can be optimized for torque guiding, and the spring element can be optimized for generating bearing clamping force.

[0029] In a favorable design, the armature plate and the drive component are arranged so that they cannot rotate relative to each other but can move along the axial direction.

[0030] In particular, the spring element arranged between the driving member and the armature plate, especially the spring plate connected to the driving member by means of the first connecting element and to the armature plate by means of the second connecting element, generates a spring force acting on the armature plate and pointing towards the driving member.

[0031] In particular, the spring element is supported on the driving component.

[0032] In particular, the connecting element is implemented as a rivet. The advantage of this is that the armature plate can be easily connected to the driving component via the spring plate and the connecting element.

[0033] In an advantageous design, a coil is incorporated within the magnet, particularly in the radial direction between the inner and outer rings of the magnet. The advantage here is that, in relation to powering the coil, a reverse magnetic field relative to the magnetic field generated by the permanent magnet can be generated, resulting in a smaller magnetic flux flowing through the armature when the coil is powered compared to when it is not powered. Consequently, when the coil is not powered, the armature is attracted to the magnet by the spring force generated by the spring plate, and when the coil is powered, the armature is pulled away from the magnet by the spring force.

[0034] In an advantageous design, the magnet has an outer ring and an inner ring.

[0035] In this configuration, a permanent magnet is arranged between the inner and outer rings, particularly axially. The advantage is that the magnetic flux from the north pole of the permanent magnet passes through the inner ring and flows directly or through an air gap to the armature, and directly or through an air gap to the outer ring, and from the outer ring to the south pole. Alternatively, the north and south poles are interchanged. However, regardless of the configuration, a spacer ring / interval ring bridging the permanent magnet prevents the inner ring from approaching the outer ring. Preferably, the spacer ring is radially positioned outside the permanent magnet and / or made of a diamagnetic material, particularly plastic.

[0036] In one advantageous design, the outer ring of the first bearing abuts against a stepped portion formed at the magnet, particularly at the inner ring of the magnet.

[0037] In this configuration, the inner ring of the first bearing abuts against a stepped portion formed on the shaft. Advantageously, the first bearing is implemented as a fixed bearing, but the magnet can move axially relative to the housing member, while the second bearing is arranged so that it cannot move relative to the housing member, because the second bearing is also implemented as a fixed bearing.

[0038] Preferably, the rotor is rotatably supported only by the first and second bearings.

[0039] In an advantageous design, especially when the coil is powered, the magnetic flux passing through the armature is reduced compared to when the coil is not powered. The advantage here is that the braking effect is controllable.

[0040] In an advantageous design, the outer ring of the magnet is axially movable within the receiving element. The advantage here is that variations in the length of the housing and rotor due to heat have almost no impact on the angle detection of the angle sensor, which is positioned closer to the first bearing than the second bearing.

[0041] In an advantageous design, the rotor shaft of the angle sensor is connected to the rotor in a manner that prevents relative rotation, and the housing of the angle sensor is connected to the first region of the second torque support, wherein the second region of the second torque support is connected to the inner ring of the magnet, specifically pressed against the inner ring of the magnet together with an auxiliary plate by means of screws.

[0042] In particular, compared to the first region, the second region is arranged at a greater radial distance, and specifically, it is arranged further outward radially compared to the first region. The advantage of this is that angle detection can be performed independently of temperature, because when the rotor length changes relative to the housing and thus causes axial movement of the first bearing, it can be said that the angle sensor is actuated.

[0043] In an advantageous design, the radial range covered by the first torque support is spaced apart from the radial range covered by the second torque support, and / or the radial range covered by the first torque support is arranged radially outside the radial range covered by the second torque support. The advantage here is that the first torque support functions independently of the second torque support, and higher torque can be transmitted while maintaining a compact implementation.

[0044] In an advantageous design, the first torque support has an inner ring region, an outer ring region, and a bridging portion connecting the inner and outer ring regions, the bridging portions being spaced apart from each other, particularly uniformly in the circumferential direction.

[0045] The inner ring region rests against the inner ring of the magnet, while the outer ring region rests against the receiving component or housing component.

[0046] Among them, or

[0047] - The maximum circumferential angle value of the circumferential angle range covered by the corresponding bridging part at a radial distance increases monotonically, especially strictly monotonically, with the increase of radial distance, that is, especially in the circumferential direction.

[0048] Furthermore, the minimum circumferential angle value within this circumferential angle range increases monotonically, and especially strictly monotonically, with increasing radial distance; that is, it increases particularly in the circumferential direction.

[0049] or

[0050] - The maximum circumferential angle value of the range of circumferential angles covered by the corresponding bridging part at a radial distance decreases monotonically, and especially strictly monotonically, as the radial distance increases.

[0051] Furthermore, the minimum circumferential angle value within this circumferential angle range decreases monotonically, and especially strictly monotonically, as the radial distance increases.

[0052] The advantage here is that the torque support is particularly effective and / or robust in the preferred direction of rotation. Therefore, when the rotor is operated in only one direction of rotation, braking torque can be efficiently guided through the torque support—especially in the direction of rotation—during braking.

[0053] In one advantageous design, a bellows supported on the receiving element presses the inner ring of the magnet, particularly the stepped portion formed on the inner ring of the magnet, against the outer ring of the first bearing, causing the inner ring of the first bearing to press the driving element against the stepped portion formed on the rotor. The advantage here is that the bellows achieves a torque support function, i.e., guides the reaction torque and generates a bearing clamping force.

[0054] In another advantageous design, a spring element supported at the receiving part, the housing part, or a ring fixedly connected to the receiving part or the housing part presses the inner ring of the magnet, especially the stepped portion formed on the inner ring of the magnet, against the outer ring of the first bearing, so that the inner ring of the first bearing presses the driving element against the stepped portion formed on the rotor. The advantage here is that the spring element can be optimized for generating the bearing clamping force, and the torque support can be optimized for guiding the reaction torque.

[0055] In an advantageous design, particularly before the flange and reducer are connected to the housing, the outer ring of the second bearing is housed in an isolator, especially one made of glass fiber reinforced plastic.

[0056] The insulating member is received within the housing component, particularly within an annular groove that surrounds the housing component in the circumferential direction.

[0057] The flange is positioned on the side of the isolator opposite to the first bearing. This arrangement allows for performance testing of the motor before assembling the reducer and flange. For this purpose, the outer ring of the second bearing is housed within the isolator.

[0058] In an advantageous design, the first portion of the area covered axially by the outer ring of the second bearing contacts the flange, and

[0059] The second portion of the area covered in the axial direction by the outer ring of the second bearing contacts the insulating element.

[0060] In this configuration, the first region is spaced apart from or adjacent to the second region, and more importantly, the first and second regions do not overlap. The advantage of this is that performance testing can be performed before the flange is installed, and the second bearing also functions as a stationary bearing after the flange is installed. Here, when the flange is installed, the second bearing moves axially against the spring force generated by the spring element.

[0061] For those skilled in the art, in particular, other reasonable combinations of features of the specification and / or drawings can be derived from the objective setting and / or the objective proposed by comparison with the prior art. Attached Figure Description

[0062] The invention will now be explained in detail with reference to the schematic diagram.

[0063] exist Figure 1 The drive device according to the invention is shown in cross-section, which has a reducer driven by a brake motor, wherein a bellows 40 is provided as a torque support to generate a bearing clamping force for the bearing assembly of the rotor 9 of the brake motor.

[0064] exist Figure 4 The image is shown in an enlarged format. Figure 1 A part of it.

[0065] exist Figure 3 The torque support is shown in a top view.

[0066] exist Figure 2 The diagram shows a portion of another drive device according to the invention, wherein a first torque support 10 for the braking assembly is provided instead of a bellows 40. Detailed Implementation

[0067] As in Figure 2 and Figure 3 As shown, the motor has a rotor 9, which is axially supported on both sides by means of fixed bearings and is connected to the rotor shaft of the angle sensor 15 in a manner that prevents relative rotation at the end region of the first axial direction of the rotor.

[0068] At the end region of its separation from the angle sensor 15, the rotor 9 is connected to the sun gear of the planetary gear stage of the reducer in a manner that prevents relative rotation. In particular, the sun gear is connected to the rotor 9 as an insert pinion.

[0069] The planetary gear meshes with the sun gear, is rotatably supported on a planet carrier, and meshes with a ring gear connected to the reducer housing. The planet carrier serves as the output shaft of the planetary gear transmission stage. The reducer housing is connected to a flange 22, which receives one of the bearings of the rotor 9. This bearing is implemented as a fixed bearing. For this purpose, the flange 22 has a stepped portion, against which the outer ring of the bearing rests. The inner ring of the bearing rests against the stepped portion constructed at the rotor 9.

[0070] The area covered by the bearing 24 in the axial direction, that is, in the direction parallel to the rotation axis of the rotor 9, overlaps with the area covered by the sun gear, which is configured to insert a pinion.

[0071] And / or,

[0072] The area covered by the flange 22 in the axial direction, that is, in the direction parallel to the rotation axis of the rotor 9, overlaps with the area covered by the sun gear that is configured to insert a pinion.

[0073] Furthermore, a retainer 23 for thermal and electrical separation and for receiving the bearing used for performance testing is received in the housing 1. For this purpose, an inner groove is introduced into the housing 1, and the retainer 23 is inserted into this inner groove. The retainer 23 also receives the outer ring of the bearing 24. However, the retainer 23 does not have a stepped portion, so that the bearing 24 is not axially restricted by the retainer 23.

[0074] Preferably, the insulating member 23 is made of glass fiber reinforced plastic and thus has sufficiently high stability to enable performance testing of the motor in the absence of a reducer and, consequently, a flange member 22. However, only no-load operation of the motor can be used for performance testing.

[0075] The inner ring of bearing 24 fits into the bearing housing precision-machined at rotor 9 and abuts against the stepped portion of rotor 9. The outer ring of bearing 24 is inserted into the recess of the isolator 23, and if the outer ring is not received in flange 22 or abuts against the stepped portion of flange, the bearing is therefore not axially fixed.

[0076] Therefore, during manufacturing, only performance tests can be performed during the no-load operation of the motor, but load tests cannot be conducted.

[0077] Because the bearings are arranged very close to the sun gear connected to the rotor 9, the thermal expansion of the rotor 9 and / or housing 1 will not cause significant angular changes at the sun gear and the planetary gear meshing with the sun gear.

[0078] The first bearing 8 of the rotor 9 is also implemented as a fixed bearing. Not only the inner ring of the first bearing 8 but also the outer ring of the bearing 8 are axially restricted. For this purpose, a stepped portion is preferably formed at the rotor 9, wherein the inner ring of the first bearing 8 is axially arranged next to the drive member 7, and the drive member abuts against the stepped portion of the rotor 9.

[0079] The outer ring of the first bearing 8 is received in the inner ring 13 of the magnet of the braking assembly arranged at the motor and abuts against the stepped portion of the inner ring 13 of the magnet.

[0080] The magnet consists of an inner ring 13 and an outer ring 3. A coil 6 is fitted onto the inner ring 13 of the magnet, and current can be applied to the coil 6 through the power supply line 18, thereby powering the coil 6.

[0081] The coil 6 is arranged radially inside the outer ring 3 of the magnet and radially outside the inner ring of the magnet.

[0082] The receiving part 2, especially the brake bearing cover, is fixed to the housing part 1. The magnet having the coil 6 contained therein is received in the receiving part 2.

[0083] In order to preload the bearing assembly consisting of the first bearing 8 and the second bearing, the spring element 12, supported on the ring 11 connected to the receiving member 2, presses the inner ring 13 of the magnet against the outer ring of the first bearing 8 and thereby presses it toward the second bearing 24.

[0084] Thus, the spring element 12 preloads the bearing assembly. Therefore, even if the housing 1 expands more dramatically than the rotor 9 due to heat, the bearing assembly remains preloaded. Even though the rotor 9 is supported in two fixed bearings, the bearing assembly is protected from high stress.

[0085] Furthermore, it does not interfere with the function of the brake.

[0086] A permanent magnet 14 is also arranged between the outer ring 3 and the inner ring 13 of the magnet. The magnetic flux of the permanent magnet is guided to the armature plate 4 through the outer ring 3 and then to the inner ring 13 of the magnet by the armature plate 4.

[0087] A spring plate, axially arranged between the armature plate 4 and the drive member 7, is fixed to the armature plate 4 by a first connecting element 5, particularly a rivet. The spring plate is fixed to the drive member 7 by a second connecting element, particularly a rivet. The spring plate exerts a reaction force on the armature plate 4, moving it away from the drive member 7. This is because as the distance between the armature plate 4 and the drive member 7 increases, the spring force pulls the armature plate 4 back, i.e., towards the drive member 7, with increasing force. However, the magnetic force of the permanent magnet 14 overcomes the spring force generated by the spring plate.

[0088] When the coil 6 is not powered, in order to reduce the air gap between the armature 4 and the magnet, the armature 4 is attracted to the magnet, so that the armature 4, which is connected to the drive 7 or the rotor 9 in a manner that prevents relative rotation, is pressed onto the magnet and thereby generates a braking torque.

[0089] When the coil 6 is powered, a magnetic field opposite to that generated by the permanent magnet is generated, so less or even no magnetic flux flows through the armature plate 4 and thus the armature plate is axially pulled away from the magnet by means of the spring plate.

[0090] Therefore, the armature plate 4 and the rotor 9 are connected in a manner that prevents relative rotation, but are arranged to allow axial movement.

[0091] A torque support 10, secured to the receiving element with screws—especially with fewer screws—is connected to the inner ring of the magnet. This directs the reaction torque of the braking assembly to the housing.

[0092] Preferably, the torque support 10 is axially arranged between the receiving member 2 and the spring element 12.

[0093] The rotor shaft of the angle sensor 15 is connected to the rotor 9 in a manner that prevents relative rotation, and is arranged to rotate relative to the housing of the angle sensor 15. The housing of the angle sensor is supported on the inner ring 13 of the magnet by means of a second torque support 16. For this purpose, the second torque support 16 is pressed against the inner ring 13 of the magnet by a screw screwed into an axially pointing threaded hole in the inner ring 13 of the magnet, especially by the head of the screw.

[0094] In addition, an auxiliary plate 17 with an internal hexagonal shape is fixed on the inner ring 13 of the magnet as an assembly aid for the screw.

[0095] During assembly, the auxiliary plate 17 is first pushed onto the outer hexagonal region of the rotor shaft of the angle sensor 15 via its inner hexagonal shape in a form-locking manner, thereby allowing the rotor shaft of the angle sensor to be easily screwed into the rotor 9. After the auxiliary plate 17 is pressed against the inner ring 13 of the magnet by means of screws, the form-locking hexagonal connection is loosened by axially moving the auxiliary plate 17, thereby rendering the auxiliary plate 17 inactive. However, the screws pass through the auxiliary plate 17 and the second torque support 16, thereby arranging the second torque support 16 further away from the housing of the angle sensor 15 in the axial direction. In this way, although the second torque support is implemented to be very rigid in the circumferential direction, it is flexible in the axial direction.

[0096] As in Figure 3As shown, the first torque support has an inner ring region 33 arranged radially within the outer ring region 34, wherein circumferentially spaced bridging portions connect the inner ring region 33 to the outer ring region 34.

[0097] A first hole 30 is provided at the outer ring region 34, through which the first torque support 10 passes, and the screw that is screwed into the receiving member 2 passes through the first hole.

[0098] A second hole 31 is provided at the inner ring region 33, passing through the first torque support 10, and a screw screwed into the inner ring of the magnet passes through this second hole.

[0099] The bridging portion 32 gradually extends in the circumferential direction as the radial distance increases.

[0100] That is, in particular, the range of circumferential angles covered by the corresponding bridging portion 32 at the corresponding radial distance shifts along the circumferential direction in a manner that increases in the radial direction. Preferably, the width of the bridging portion 32, measured in the circumferential direction, is constant at any radial distance.

[0101] As in Figure 1 and Figure 4 As shown in the figure, unlike the above embodiment, a bellows 40 is provided, which replaces the spring element 12, the first torque support 10, and the ring 11.

[0102] The bellows 40 is pressed against the inner ring 13 of the magnet by means of the second screw 42, and against the receiving member 2 by means of the first screw 41. The spring force generated by the bellows 40 acts in the axial direction and generates a spring force from the inner ring 13 of the magnet toward the second bearing, i.e., toward the reducer.

[0103] In order to supply power to the brake motor, especially the stator winding 21, a plug-in connector 19 is arranged at the housing part 1.

[0104] The housing cover 20 is connected to the housing part 1 and also protects the stator winding 21.

[0105] The bellows 40 is preferably implemented as a metal bellows, and the radially inner end region of the bellows has a reinforcement, i.e., a greater wall thickness. When manufacturing the metal bellows 40 from a sheet of material with a constant wall thickness, the reinforcement region can be created, for example, by crimping the sheet and thus creating a double layer. Alternatively, the annular members can also be welded together.

[0106] The first bearing 8 and the second bearing 24 are respectively implemented as rolling bearings, especially ball bearings.

[0107] In other embodiments of the invention, the spring plate is replaced by another spring element or another spring assembly.

[0108] In other embodiments of the invention, instead of multiple spring elements 12, a single spring element or at least one group of springs is used. Here, the first connecting element 5 can also be used to connect the armature plate 4 to the drive member 7.

[0109] List of reference numerals in the attached diagram:

[0110] 1. Housing components

[0111] 2. Receiving components, especially brake bearing caps

[0112] 3 Outer Ring

[0113] 4 Armature Plate

[0114] 5. Connecting elements, especially rivets

[0115] 6 coils

[0116] 7. Drive components

[0117] 8. First bearings, especially ball bearings

[0118] 9. The rotor of the electric motor

[0119] 10 Especially for the first torque support member used in braking assemblies

[0120] 11 rings

[0121] 12 Spring elements, especially spring assemblies

[0122] 13 Inner Ring

[0123] 14 permanent magnets

[0124] 15 Angle Sensors

[0125] 16 In particular, the second torque support for the angle sensor 15

[0126] 17. An auxiliary plate with an internal hexagonal shape, used as an assembly aid.

[0127] 18. Power supply line for coil 6

[0128] 19. Plug-in connectors

[0129] 20. Housing cover

[0130] 21 Stator windings

[0131] 22 Flange components, especially bearing flanges

[0132] 23 Isolation components used for thermal and electrical separation and for housing bearings used for performance testing

[0133] 24 Second Bearing

[0134] 30 First Hole

[0135] 31 Second hole

[0136] 32 Bridging section

[0137] 33 Inner Ring Area

[0138] 34 Outer Ring Area

[0139] 40. Corrugated pipes, especially metal corrugated pipes

[0140] 41 First screw

[0141] 42 Second screw

Claims

1. A drive device having a motor equipped with a braking component, The electric motor has a housing and a rotor that is rotatably supported by a first bearing and a second bearing. The first bearing has an inner ring and an outer ring. The inner ring of the first bearing is fitted onto the rotor or pressed against the driving component, which abuts against a stepped portion formed on the rotor. The braking assembly has a magnet made of a ferromagnetic material. Its features are, The outer ring of the first bearing is housed within the magnet of the braking assembly. The magnet is received in a receiving member that is fixedly connected to the housing member or is housed within the housing member. The magnet is arranged to move along the axial direction and is connected to the first torque support. The first torque support is connected to the receiving part and / or the housing part. The first torque support is implemented as a bellows, wherein the area of ​​the contact receiver of the first torque support is spaced apart from the area of ​​the contact magnet in the axial direction, and the area of ​​the contact magnet is arranged at a smaller radial distance compared to the area of ​​the contact receiver. or, The first torque support is implemented as a plate, such that the area of ​​the contact receiving part of the first torque support is arranged at the same axial position as the area of ​​the torque support that is contacted by the magnet, and the area that is contacted by the magnet is arranged at a smaller radial distance than the area of ​​the contact receiving part.

2. The driving device according to claim 1, characterized in that, The outer ring of the second bearing is received in the housing or in a flange that is connected to the housing component. The inner ring of the second bearing is fitted onto the rotor.

3. The driving device according to claim 1 or 2, characterized in that, The armature and the driving component are arranged so that they cannot rotate relative to each other but can move along the axial direction. The spring element arranged between the driving member and the armature plate is constructed as a spring plate connected to the driving member by means of a first connecting element and to the armature plate by means of a second connecting element. This spring element generates a spring force acting on the armature plate and pointing towards the driving member. The spring element is supported on the driving component. The first connecting element and the second connecting element are implemented as rivets.

4. The driving device according to claim 1 or 2, characterized in that, A coil is accommodated in the magnet in the radial direction between the inner and outer rings of the magnet. And / or, The magnet has an outer ring and an inner ring. Permanent magnets are arranged between the inner and outer rings in the axial direction.

5. The driving device according to claim 1 or 2, characterized in that, The outer ring of the first bearing abuts against a stepped portion formed at the magnet, the stepped portion being formed at the inner ring of the magnet. The inner ring of the first bearing abuts against the stepped portion formed on the shaft.

6. The driving device according to claim 3, characterized in that, Compared to when the coil is not powered, the magnetic flux passing through the armature plate is reduced when the coil is powered.

7. The driving device according to claim 4, characterized in that, The outer ring of the magnet is arranged in the receiving part in a manner that allows it to move axially.

8. The driving device according to claim 1 or 2, characterized in that, The rotor shaft of the angle sensor is connected to the rotor in a manner that prevents relative rotation. The housing of the angle sensor is connected to the first region of the second torque support member. The second region of the second torque support member is connected to the inner ring of the magnet. The second region of the second torque support member, together with the auxiliary plate, is pressed against the inner ring of the magnet by screws. Compared to the first region, the second region is arranged at a greater radial distance and is arranged further out in the radial direction compared to the first region.

9. The driving device according to claim 8, characterized in that, The radial range covered by the first torque support is spaced apart from the radial range covered by the second torque support, and / or the radial range covered by the first torque support is arranged radially outside the radial range covered by the second torque support.

10. The driving device according to claim 1 or 2, characterized in that, The first torque support member has an inner ring region, an outer ring region, and a bridging portion connecting the inner ring region and the outer ring region. The inner ring region rests against the inner ring of the magnet, while the outer ring region rests against the receiving component or housing component. Among them, or - The maximum circumferential angle value of the range of circumferential angles covered by the corresponding bridging part at a radial distance increases strictly monotonically with the increase of radial distance. Furthermore, the minimum circumferential angle value within the range of circumferential angles increases strictly monotonically with increasing radial distance. or, - The maximum circumferential angle value of the circumferential angle range covered by the corresponding bridging part at a radial distance decreases strictly monotonically as the radial distance increases. The minimum circumferential angle value of the circumferential angle range decreases strictly monotonically as the radial distance increases.

11. The driving device according to claim 1 or 2, characterized in that, The bellows supported on the receiving component presses the inner ring of the magnet against the outer ring of the first bearing, causing the inner ring of the first bearing to press the driving component against the stepped portion formed on the rotor. or, A spring element supported at the receiving part, the housing part, or a ring fixedly connected to the receiving part or the housing part presses the inner ring of the magnet against the outer ring of the first bearing, so that the inner ring of the first bearing presses the drive element against the stepped portion formed on the rotor.

12. The driving device according to claim 2, characterized in that, Before the flange and reducer are connected to the housing, the outer ring of the second bearing is received in an isolator made of glass fiber reinforced plastic. The isolation element is housed within the housing element. The flange is located on the side of the isolator opposite to the first bearing.

13. The driving device according to claim 2, characterized in that, The first portion of the area covered in the axial direction by the outer ring of the second bearing contacts the flange. The second portion of the area covered in the axial direction by the outer ring of the second bearing contacts the insulating element. The first region is separated from or adjacent to the second region, and the first region and the second region do not overlap.

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