CN215950197U - Drive device - Google Patents

Abstract

The utility model relates to a drive device having a retarder with a retarder housing, an electromagnetically actuable brake device and an electric motor, wherein the brake device is arranged between the retarder and the electric motor, wherein a first bearing is accommodated in a first housing part of the brake device, wherein a second bearing is accommodated in a second housing part of the brake device, wherein the shaft is rotatably supported by means of the first bearing and the second bearing, wherein the shaft is connected in a rotationally fixed manner to a toothed part of the retarder, wherein the shaft passes through a magnet body of the brake device, wherein the shaft is connected in a rotationally fixed manner to a brake lining carrier, which is arranged in the axial direction between the first bearing and the second bearing.

Description

Drive device

Technical Field

The utility model relates to a drive device having a retarder with a retarder housing, an electromagnetically actuable brake device and an electric motor.

Background

It is generally known that the drive means can be constructed by a speed reducer driven by an electric motor.

SUMMERY OF THE UTILITY MODEL

The object of the utility model is therefore to achieve low operating costs in the drive.

According to the utility model, this object is achieved by a drive device having the following features.

In the case of a drive device, an important feature of the utility model is that the drive device has a retarder with a retarder housing, an electromagnetically actuable braking device and an electric motor, wherein the braking device is arranged between the retarder and the electric motor,

wherein a first bearing is received in a first housing part of the brake device and a second bearing is received in a second housing part of the brake device,

wherein the shaft is rotatably supported by means of a first bearing and a second bearing,

wherein the shaft is connected in a rotationally fixed manner to a toothed part of the gear unit, in particular to a toothed part of a first gear stage of the gear unit, in particular a nested pinion, or is formed in one piece, in particular integrally, with the toothed part,

wherein the shaft passes through the magnet body of the braking device, in particular through the ferromagnetic coil body of the braking device,

wherein the shaft is connected in a rotationally fixed manner to a brake lining carrier/brake pad carrier, which is arranged in the axial direction between the first bearing and the second bearing,

in particular wherein the brake lining carrier is arranged to be movable relative to the shaft, in particular to be movable parallel to the axis of rotation of the shaft.

The advantage here is that the operating costs are low, since maintenance can also be carried out by personnel without special training. In particular, the brake device is encapsulated against explosion pressure/explosion and is therefore only allowed to be opened by specially trained personnel. However, the entire brake device can be removed from the drive device by untrained personnel and replaced with another brake device.

Thus, cost-effective maintenance can be achieved. Furthermore, the person also has the right to maintain the motor and the retarder, i.e. in particular also to open the retarder and replenish the oil or replace the toothed parts of the retarder.

Furthermore, the braking device itself can be equipped with a wear sensor, so that maintenance or replacement can be carried out in a timely manner. Furthermore, the angle sensor can be integrated into the brake device, thereby increasing the operational safety and thus also reducing the operating costs, in particular by timely maintenance and damage prevention.

It is also important that the brake lining carrier is arranged to be movable and that the braking action is therefore substantially independent of the state of wear of the brake lining carrier. Since minor wear can be compensated for by means of the movement. This also increases the operational safety.

In an advantageous embodiment, the first housing part is connected to the second housing part, in particular wherein the contact region of the first housing part to the second housing part extends in the axial direction longer than in the radial direction. The advantage here is that the brake can be arranged in a housing that is resistant to explosion pressure. The brake is therefore arranged in a sealed manner and can be arranged as a transportable unit between the electric motor and the retarder.

In an advantageous embodiment, the shaft is connected to a rotor shaft of the electric machine in a rotationally fixed manner. The advantage here is that the shaft can be connected to the rotor shaft via a coupling, in particular a claw coupling. Thus, the coupling function can be integrated into the brake device. The braking device thus also serves as an adapter between the electric machine and the retarder, wherein the braking device, for example, balances and/or compensates for deviations of the axis of rotation of the rotor shaft from the axis of rotation of the shaft.

In an advantageous embodiment, the shaft has claws spaced apart from one another in the circumferential direction on its axial end region facing the rotor shaft,

wherein the coupling part is connected in a rotationally fixed manner to the rotor shaft, in particular by means of a key connection,

wherein the coupling has, on its axial end region facing the shaft, claws spaced apart from one another in the circumferential direction,

wherein a region covered by the claw of the coupling member in the axial direction overlaps with a region covered by the claw of the shaft in the axial direction,

in particular, the radial distance region covered by the claws of the coupling member with reference to the axis of rotation of the shaft is also covered by the claws of the shaft. The advantage here is that tolerance compensation can be brought about by means of the coupling. Thus, if the axes of rotation of the rotor shaft and the shaft are not precisely aligned with each other, the coupling effects the transmission of torque and dampens transverse moments. Furthermore, a plastic material, in particular a plastic material of a star-shaped plastic star, can be arranged between the claws, so that rotational speed fluctuations are suppressed.

In an advantageous embodiment, the brake lining carrier is arranged so as to be axially movable relative to the shaft, in particular wherein a driver/follower is mounted on the shaft, which driver is positively connected in the circumferential direction to the shaft and/or which driver is positively connected to the shaft by means of a key connection,

the driver has an external toothing which meshes with an internal toothing of the brake lining carrier. The advantage here is that the brake lining carrier temporarily compensates for the wear of the brake lining by moving. Since the spring element presses the brake lining carrier via the armature plate correspondingly closer to the friction lining in the case of thinner brake linings and no current flow in the coil. Therefore, the operation safety is high. Furthermore, sensors, in particular microswitches or inductive proximity sensors, arranged on the brake are used to monitor whether the wear exceeds an allowable level. In this way, the operational safety is also further increased.

In an advantageous embodiment, the armature plate is connected to the magnet body in a rotationally fixed but axially movable manner,

wherein a spring element supported on the magnet body presses against the armature plate, in particular exerts a spring force on the armature plate,

wherein the armature plate is arranged between the magnet body and the brake lining carrier, in particular axially,

in particular, the magnet body and/or the armature plate is made of a ferromagnetic material. The advantage here is that the operating safety is increased, since the brake automatically engages in the event of a current failure of the coil.

In an advantageous embodiment, the friction lining is connected to the magnet body, in particular by means of a pin which projects into the magnet body and guides the armature plate,

in particular, the friction lining is connected to the first housing part. The advantage here is that the brake can be designed as a prefabricated unit and thus the safety is increased.

In an advantageous embodiment, the brake, which comprises the magnet body, the coil, the spring element, the armature plate, the brake lining carrier, the friction lining and the pin, is designed as a prefabricated unit. The advantage here is that the brake can be mounted already before being installed in the housing of the brake device and can be stored as a functional unit in a warehouse and subsequently installed in the housing. During assembly, the friction lining is connected to the first housing part of the housing of the brake device by means of a screw. In this case, the circuit board is preferably clamped between the friction lining and the first housing part.

In an advantageous embodiment, the magnet body, the coil, the spring element, the armature plate, the brake lining retainer, the friction lining and the pin are enclosed by a housing formed by the first housing part and the second housing part, and/or the housing formed by the first housing part and the second housing part forms a housing for the magnet body, the coil, the spring element, the armature plate, the brake lining retainer, the friction lining and the pin. The advantage here is that the brake can be mounted already before being installed in the housing of the brake device and can be stored as a functional unit in a warehouse and subsequently installed in the housing. During assembly, the friction lining is connected to the first housing part of the housing of the brake device by means of a screw. In this case, the circuit board is preferably clamped between the friction lining and the first housing part.

In an advantageous embodiment, the rotary part is rotatably mounted relative to the first housing part, in particular about a rotational axis oriented perpendicularly to the rotational axis of the shaft,

wherein the rotating member has an eccentric area,

wherein in a first rotational position of the rotor the eccentric region presses the armature plate against the spring force generated by the spring element against the magnet body, and in a second rotational position of the rotor the armature plate can be moved in the axial direction, i.e. in the direction of the rotational axis of the shaft, such that the armature plate presses the brake lining carrier against the friction lining, in particular when the coil is not energized,

in particular, the rotary part is connected to the retaining clip, in particular, the retaining clip extends at least partially, in particular tangentially and/or in the circumferential direction, with respect to the axis of rotation of the shaft. The advantage here is that a manual release, i.e. a manually activatable release of the brake, can be achieved. For this purpose, the holding bracket is pivoted and the rotary part is thereby rotated, so that the eccentric part of the rotary part presses the armature plate against the magnet body, in particular against the spring force generated by the spring element.

In an advantageous embodiment, a flange part is connected to the second housing part, which covers and/or closes the opening of the gear housing, in particular in an oil-tight manner. The advantage here is that the brake device can be connected with its entire housing via a flange part to the retarder and can be held by the retarder. In particular, the electric motor can be fixed to the housing of the brake device and can be held by the housing. Furthermore, it is also possible for a person without special training to connect the brake device to the retarder and then to inject oil into the retarder. In this case, it is not necessary to open the brake enclosed in the housing of the brake device. The flange part can cover the opening of the gear unit and thus the gear unit can be filled with oil afterwards. In a further development, even the second housing part of the brake device can be used directly to cover the opening of the gear unit. Thus eliminating the need for a flange member.

In an advantageous embodiment, a lower part is connected to the outside of the first housing part, on which lower part the cover is placed, so that an electrical connection device is arranged in the terminal box formed by the lower part and the cover and forms a housing for the electrical connection device,

the electrical line is guided through a cable bushing that is resistant to explosion pressure and is arranged in a through opening of the first housing part. The advantage here is that the connection box itself is designed to be resistant to explosion pressure. Thus, the electrical terminals can be provided on the connection device and thus be arranged in the region of resistance to explosion pressure. Furthermore, this terminal block region is separate from the brake region and is connected only by cable feedthroughs. The explosion cannot therefore propagate from the region of the brake to the region of the connecting device, and conversely also from the region of the connecting device to the region of the brake. Thus improving safety.

In an advantageous embodiment, the first printed circuit board is connected in a rotationally fixed manner to the first housing part,

wherein the second circuit board, namely the other circuit board, is connected with the shaft in a mode of relative rotation,

wherein the first circuit board is equipped with electronic components, such that the angular position of the second circuit board and/or the shaft can be detected,

in particular, the first printed circuit board is arranged parallel to the second printed circuit board and/or the first printed circuit board is pressed against the first housing part by the friction lining, in particular the second printed circuit board is arranged axially between the first printed circuit board and the first housing part. The advantage here is that the first printed circuit board can be arranged in a clamping manner and can therefore be connected in a cost-effective manner.

In an advantageous embodiment, the sensor for detecting wear of the brake lining/brake pad is arranged in a housing formed by the first housing part and the second housing part,

in particular, the sensor line is guided through the cable leadthrough. The advantage here is that maintenance can be carried out in a timely manner.

In an advantageous embodiment, an annular gap is arranged between the first housing part and the shaft,

in particular, the axial length of the annular gap is greater than the radius of the annular gap,

the annular gap is arranged on the side of the first bearing facing away from the magnet body and/or the second bearing, in particular on the side of the first bearing facing away from the magnet body and/or the second bearing in the axial direction. The advantage here is that the annular gap is designed so narrow and so long in the axial direction that penetration of the explosion front (explosion front) is prevented. Furthermore, the first bearing can be arranged in the region of resistance to explosion pressure and thus the operational safety is increased, since the rotatability of the shaft is reliably ensured.

In an advantageous embodiment, the second bearing is designed as a double bearing, in particular wherein the second bearing has at least a cylindrical roller bearing. The advantage here is that, for example, transverse forces occurring in the first gear stage can be dissipated via the double bearing, and therefore the annular gap arranged between the shaft and the second housing part does not change its thickness, in particular not to a measurable extent, even in the event of fluctuations in the transverse forces.

In an advantageous embodiment, a further annular gap is arranged between the second housing part and the shaft,

in particular, the axial length of the further annular gap is greater than the radius of the further annular gap,

wherein the second bearing is arranged on a side of the further annular gap facing away from the magnet body and/or the first bearing, in particular on a side of the further annular gap facing away from the magnet body and/or the first bearing in the axial direction. The advantage here is that the second bearing is accessible and replaceable from the outside without having to open the housing of the brake device. It is therefore no longer necessary to resort to specially qualified professionals. Even if the transverse forces fluctuate, the further annular gap does not change its thickness, in particular not to a measurable extent.

The utility model is not limited to the above-described combination of features. The above-described combinations of features and/or individual features described above and/or features to be described below and/or other possible combinations of features and/or figures can be made possible by those skilled in the art, in particular as a result of the objects set forth and/or as a result of comparison with the prior art.

Drawings

The utility model will now be described in detail with reference to the schematic drawings:

fig. 1 shows a cross section of a braking device according to the utility model.

Fig. 2 shows a cut-away oblique view of the brake device of fig. 1.

Fig. 3 shows a cross section of another brake device.

Fig. 4 shows an oblique view of the braking device of fig. 3.

List of reference numerals:

1 Flange part

2 axle

3 magnet body

4 coil

5 armature sheet

6 brake lining support

7 Friction disk

8 first housing part

9 first bearing

10 coupling piece

12 first circuit board

13 permanent magnet

14 cable through pipe

15 lower part

16 Electrical connection device

17 cover

19 second housing part

20 second bearing

21 clamp

22 rotating part

23 entrainment member

30 spring element

40 bearing seat

41 support rib

Detailed Description

As shown in the drawing, the brake device according to the utility model is designed to be resistant to explosion pressure.

The brake device may be arranged between the electric machine and the retarder, wherein the brake device is held by the retarder housing. The rotor shaft of the electric machine can be connected in a rotationally fixed manner to the coupling piece 10.

For example, the coupling piece 10 is sleeve-shaped and is slipped onto a rotor shaft, not shown in the figures, and is connected to the rotor shaft in a rotationally fixed manner, in particular by means of a key connection.

The shaft 2 of the brake device is connected in a rotationally fixed manner to a toothed part of the gear unit, in particular to a toothed part of the first gear stage of the gear unit.

For this purpose, the shaft 2 has a keyway, so that a sleeve pinion can be sleeved onto the shaft 2 and can be connected to it in a rotationally fixed manner by means of a key. The nested pinion has external teeth and functions as the input toothed member of the first gear stage of the reducer.

The shaft 2 has claws on its axial end facing away from the reduction gear and/or the toothed element, which claws are operatively connected as claw couplings to claws formed on the coupling element 10. For this purpose, the claws of the shaft 2 are spaced apart from one another in the circumferential direction, in particular regularly spaced apart from one another, and project into the gaps which are produced by the spacing of the claws of the coupling 10 which is implemented in the circumferential direction. In this way, the shaft 2 is positively connected in the circumferential direction to the coupling piece 10.

The shaft 2 is rotatably mounted by means of a first bearing 9 received in the first housing part 8 and by means of a bearing 20 received in the second housing part 19.

The flange part 1 is connected to the second housing part 19 and is used for connection to a gear unit. For this purpose, the flange part 1 is connected to the gear housing by means of screws.

When the flange part 1 is connected to the gear housing, the opening of the gear housing is closed in an oil-tight manner. The flange part 1 holds a second housing part 19, which is connected to the first housing part 8, which in turn is connected to the housing of the electric machine. The electric machine is thus held on the retarder by the braking device.

The pressure-resistant, explosion-proof embodiment of the housing of the brake device therefore results in high stability and rigidity. Thus, the weight of the motor can be borne by the housing of the brake device.

A shaft sealing ring received in the second housing part 19 seals towards the shaft 2.

A sleeve-shaped driver 23 is inserted onto the shaft 2 and is connected to the shaft 2 in a rotationally fixed manner, in particular by means of a key connection. The driver has an outer toothing on its radial outer circumference, onto which the brake lining carrier 6 is pushed, wherein the inner toothing of the brake lining carrier 6 meshes with the outer toothing. In particular, the brake lining carrier 6 is therefore connected in a rotationally fixed manner to the driver 23 and can be moved axially relative to the driver 23.

In the second housing part 19, a magnet body 3 is received, which has an annular recess in which a coil, in particular an annular winding, is received, in particular wherein the ring axis is oriented coaxially to the rotational axis of the shaft 2.

The armature plate 5 is arranged between the magnet body 3 and the brake lining carrier 6 in the axial direction, i.e. in the direction of the axis of rotation of the shaft 2.

The armature plate 5 is preferably made of a ferromagnetic material. The armature plate 5 is connected to the magnet body 3 in a rotationally fixed manner, but the armature plate 5 is arranged so as to be movable in the axial direction, i.e. in the direction of the rotational axis of the shaft 2. For this purpose, a pin is preferably inserted or screwed into an axially oriented bore of the magnet body 3, said pin being guided through a corresponding recess of the armature plate 5.

The brake lining carrier 6 preferably has brake linings on both axial sides.

The spring element 30 supported on the magnet body 3 presses onto the armature plate 5, so that when the coil 4 is not energized, the armature plate 5 is pressed against the brake lining carrier 6 by means of the spring force generated by the spring element 30. At this time, the brake lining carrier 6 is pressed by the armature plate 5 against the braking surface formed on the friction plate 7. The friction lining 7 is connected, in particular fixedly connected, to the first housing part 8.

However, when the coil 4 is energized, the armature plate 5 is pulled against the spring force generated by the spring element 30 toward the magnet body 3 and thus releases the brake.

The friction lining 7 is preferably designed in the form of a disk or a disk, so that the connection between the friction lining 7 and the first housing part 8 is uninterrupted over the entire circumference. The friction lining 7 is preferably fixedly connected to the first housing part 8.

This construction allows the elements associated with the braking function to be prefabricated and then incorporated into the housing of the braking device.

To achieve prefabrication, from

The magnet body 3 together with the spring element and the coil 4 received therein,

-a piece of armature iron,

-a pin guiding the armature plate, and

brake lining carrier

The resulting stack is constructed as a prefabricated brake by means of the connection of the friction plates 7. The brake is then inserted into the housing by connecting the friction lining 7 to the first housing part 8. The friction plates are preferably connected to the magnet body 3 by pins which are inserted into holes of the magnet body. The friction lining 7 is screwed onto the pin, for example by means of a screw. The pin is preferably axially oriented.

When the brake is installed in the housing of the brake device, the friction lining 7 is connected to the first housing part 8 by means of a screw, wherein the screw is screwed into a threaded bore of the first housing part 8.

On the side facing away from the brake lining carrier 6, the friction lining 7 has an annular recess which runs around in the circumferential direction and in which a permanent magnet 13 can be accommodated, which is arranged directly on the friction lining 7 or on the first printed circuit board 12.

The first printed circuit board 12 is held by the friction lining 7 in a manner pressed onto the first housing part 8.

The permanent magnets may be arranged either separately or on the first circuit board 12.

The other circuit board is connected to the shaft 2 in a relatively non-rotatable manner. The further circuit board is thus arranged in a relatively rotatable manner with respect to the first circuit board 12.

In operative connection with the permanent magnet, the sensor is realized by means of a circuit board, so that the angular position of the shaft 2 can be detected by the sensor.

The first circuit board 12 and/or the further circuit board are equipped with electronic components, so that a detection circuit is arranged on the first circuit board and/or the further circuit board, which enables detection of the angular position of the shaft 2.

But other operating principles may be provided which do not require permanent magnets.

In any case, however, the first printed circuit board is arranged in a rotationally fixed manner relative to the first housing part 8 and the shaft 2 is connected in a rotationally fixed manner to the other printed circuit board.

The sensor signals are guided from the first circuit board 12 by means of cables via a cable feedthrough 14 that is resistant to explosion pressure into a terminal box, which is arranged on the outside of the first housing part 8. The terminal box is formed by the placement of an annular lower part 15 on the outer side and a cover 17 placed on the lower part. An electrical connection device 16 is arranged in a terminal box formed by the lower part 15 and the cover 17, which terminal box forms a housing of the electrical connection device 16.

The terminal box itself is therefore designed to be resistant to explosion pressure.

Between the lower part 15 and the cover 17 placed thereon, a gap region is formed which is as long as possible and as thin or narrower as possible in their contact region, so that the energy which a possible blast wave loses when passing through the gap region is so much that the explosion is prevented from spreading through the gap region.

Furthermore, a seal, in particular a flat seal or an O-ring, is arranged between the cover 17 and the lower part 15.

Between the lower part 15 and the first housing part 8, in their contact region, a gap region is formed which is as long as possible and as thin or narrower as possible, so that the energy which a possible blast wave loses when passing through this gap region is so great that the explosion is prevented from spreading through the gap region.

Furthermore, a seal, in particular a flat seal or an O-ring, is arranged between the lower part 15 and the first housing part 8.

Between the claws of the shaft 2 and the claws of the coupling 10 in the circumferential direction, radial regions of a plastic star are arranged, so that rotational speed fluctuations can be suppressed.

Between the first housing part 8 and the second housing part 19 connected thereto, a gap region is formed which is as long as possible and as thin or narrow as possible in their contact region, so that the energy which a possible blast wave loses when passing through this gap region is so much that the explosion is prevented from spreading through the gap region. The gap region has for this purpose an extension in the axial direction which is parallel to the direction of the axis of rotation of the shaft 2 of at least four times the extension in the radial direction.

Furthermore, a sealing element, in particular a flat sealing element or an O-ring, is arranged between the first housing part 8 and the second housing part 19 connected thereto.

The flange part 1 is located outside the brake housing formed by the first housing part 8 and the second housing part 19 connected thereto.

The second bearing 20 is preferably designed as a ball bearing, which is also assigned a cylindrical roller bearing or a skewed bearing. The double bearing of the shaft 2 formed in this way ensures as constant an orientation of the shaft 2 as possible, in particular even when significant transverse moments are introduced into the shaft 2 by the nested pinion. This is particularly important because a very narrow, but axially long, annular gap is present between the shaft 2 and the second housing part 19, so that the explosion is prevented from spreading through the gap region. For this purpose, the annular gap preferably extends at least fifty times wider in the axial direction than in the radial direction.

Likewise, such a narrow annular gap also exists between the shaft 2 and the first housing part 8, wherein, however, the first bearing 9 of the shaft 2 is received in the first housing part 8.

The first bearing 9 is arranged on the side of the first housing part 8 facing the magnet body 3.

The double bearings and thus the second bearing 20 are arranged on the side of the second housing part 19 facing the magnet body 3. In this way, after the brake has been installed in the housing of the brake device, the housing is connected and cannot thereafter be opened by a person without sufficient training. Of course, such a person is allowed to connect the housing to the flange part 1 and to connect the flange part 1 to the gear housing and even to replace the double bearings beforehand during maintenance, without in particular having to open the housing of the brake device.

In addition, a microswitch is arranged on the brake device inside the housing of the brake device for monitoring the wear of the brake linings. With the microswitch, it is possible to monitor whether the distance of the coil 4 from the armature plate 5 is below a threshold value in the engaged state of the brake, i.e. in the currentless state of the coil 4. Thus, when the brake lining has exceeded a critical wear value, a warning signal can be generated by the microswitch. But another distance sensor may be used instead of the micro switch.

As shown in fig. 2, a manual release of the brake can be achieved. For this purpose, the bracket 21 is fastened to a rotatably mounted rotor 22 which has non-circular, in particular eccentric, sections. The rotary part 22 can thus be rotated, in particular about a rotation axis oriented perpendicularly to the rotation axis of the shaft 2, by pivoting the bracket 21. As a result of this pivoting movement, the eccentric region is pressed against the armature plate 5 in such a way that the armature plate 5 is pressed against the magnet body 3 and the brake is released.

As shown in fig. 3, it is also possible, however, without the flange part 1, to cover the opening of the gear housing by connecting the second housing part 19 to the gear housing and to seal the gear against the external ambient oil. For this purpose, in fig. 3, the second housing part 19 has a correspondingly shaped flange section facing the transmission, which is not shown in fig. 3. In contrast to the exemplary embodiment according to fig. 2, the double bearings can also be replaced by correspondingly large and stable single bearings, which has the disadvantage that the wall thickness of the second housing part 19 has to be reduced. As shown in fig. 4, the second bearing 20 is received in a bearing seat 40 formed in the second housing part 19, which is connected to the flange section by radial support ribs 41.

In other embodiments according to the utility model, the first bearing 9 is also designed as a double bearing.

Claims (29)

1. A drive device having a retarder with a retarder housing, an electromagnetically actuable brake device and an electric motor,

it is characterized in that the preparation method is characterized in that,

the braking device is arranged between the speed reducer and the motor,

a first bearing is received in a first housing part of the brake device, a second bearing is received in a second housing part of the brake device,

the shaft is rotatably supported by means of a first bearing and a second bearing,

which is connected in a rotationally fixed manner to the toothed part of the reducer, or is formed in one piece with said toothed part,

the shaft passes through the magnet body of the braking device,

the shaft is connected in a rotationally fixed manner to a brake lining carrier, which is arranged in the axial direction between the first bearing and the second bearing,

the brake lining carrier is arranged to be movable relative to the shaft.

2. A drive arrangement according to claim 1, characterised in that the shaft is connected in a rotationally fixed manner to a toothed member of the first gear stage of the reduction gear.

3. A drive arrangement according to claim 2, wherein the toothed member of the first gear stage of the speed reducer is a nested pinion.

4. The drive device according to claim 1, characterized in that the magnet body is a ferromagnetic coil body of a brake device.

5. A drive arrangement according to claim 1, characterised in that a brake lining carrier is arranged to be movable relative to the shaft parallel to the axis of rotation of the shaft.

6. The drive device according to any one of claims 1 to 5,

it is characterized in that the preparation method is characterized in that,

the first housing piece is connected with the second housing piece,

the contact area of the first housing part with the second housing part extends longer in the axial direction than in the radial direction.

7. The drive device according to any one of claims 1 to 5,

it is characterized in that the preparation method is characterized in that,

the shaft is connected in a rotationally fixed manner to the rotor shaft of the electric machine.

8. The drive device as set forth in claim 7,

it is characterized in that the preparation method is characterized in that,

the shaft has claws spaced apart from one another in the circumferential direction on its axial end region facing the rotor shaft,

the coupling member is connected to the rotor shaft in a relatively non-rotatable manner,

the coupling has on its axial end region facing the shaft claws spaced apart from one another in the circumferential direction,

the area covered by the claw of the coupling member in the axial direction overlaps with the area covered by the claw of the shaft in the axial direction.

9. A drive arrangement according to claim 8, wherein the coupling member is connected in a rotationally fixed manner to the rotor shaft by means of a key connection.

10. The drive of claim 8, wherein a radial distance region covered by the jaws of the coupling with reference to the axis of rotation of the shaft is also covered by the jaws of the shaft.

11. The drive device according to any one of claims 1 to 5,

it is characterized in that the preparation method is characterized in that,

the brake lining carrier is arranged so as to be axially movable relative to the shaft, a driver is mounted on the shaft and connected to the shaft in a form-fitting manner in the circumferential direction,

the driver has an external toothing which meshes with an internal toothing of the brake lining carrier.

12. Drive device as claimed in claim 11, characterized in that the catch is positively connected to the shaft by means of a key connection.

13. The drive device according to any one of claims 1 to 5,

it is characterized in that the preparation method is characterized in that,

the armature plate is connected with the magnet body in a manner of being incapable of relative rotation and capable of axial movement,

a spring element supported on the magnet body presses against the armature plate,

the armature plate is arranged axially between the magnet body and the brake lining carrier.

14. A drive arrangement according to claim 13, wherein the magnet body and/or the armature plate is made of a ferromagnetic material.

15. The drive device as set forth in claim 13,

it is characterized in that the preparation method is characterized in that,

the friction plate is connected with the magnet body part,

the friction plate is connected with the first shell member.

16. A drive arrangement according to claim 15, wherein the friction disk is connected to the magnet body by means of a pin which projects into the magnet body and guides the armature disk.

17. The drive device as set forth in claim 16,

it is characterized in that the preparation method is characterized in that,

the brake comprising the magnet body, the coil, the spring element, the armature plate, the brake lining carrier, the friction plate and the pin is designed as a prefabricated unit,

and/or

The magnet body, the coil, the spring element, the armature plate, the brake lining holder, the friction plate, and the pin are surrounded by a housing formed by the first housing member and the second housing member.

18. The drive device as set forth in claim 13,

it is characterized in that the preparation method is characterized in that,

the rotor is mounted rotatably relative to the first housing part about a rotational axis oriented perpendicularly to the rotational axis of the shaft,

the rotating member has an eccentric area and is provided with a plurality of eccentric grooves,

in a first rotational position of the rotor, the eccentric region presses the armature plate against the spring force generated by the spring element against the magnet body, and in a second rotational position of the rotor, the armature plate can be moved in the axial direction, i.e. in the direction of the rotational axis of the shaft, so that when the coil is not energized, the armature plate presses the brake lining carrier against the friction plate.

19. The drive of claim 18,

the rotor is connected to a retaining clip which extends at least partially tangentially and/or in the circumferential direction with respect to the axis of rotation of the shaft.

20. The drive device according to any one of claims 1 to 5,

it is characterized in that the preparation method is characterized in that,

the flange part is connected to the second housing part, and covers and/or closes the opening of the gear housing.

21. The drive of claim 20, wherein the flange member closes the opening of the reducer case in an oil-tight manner.

22. The drive device according to any one of claims 1 to 5,

it is characterized in that the preparation method is characterized in that,

on the outside of the first housing part, a lower part is connected, on which the cover is placed, so that an electrical connection device is arranged in the terminal box formed by the lower part and the cover and forms a housing for the electrical connection device,

the electrical line is guided through a cable bushing that is resistant to explosion pressure and is arranged in a through opening of the first housing part.

23. The drive device according to any one of claims 1 to 5,

it is characterized in that the preparation method is characterized in that,

the first circuit board is connected with the first shell part in a relatively non-rotatable manner,

a second circuit board, i.e. the other circuit board, is connected to the shaft in a relatively non-rotatable manner,

the first circuit board is equipped with electronic components so that the angular position of the second circuit board and/or the shaft can be detected.

24. The drive of claim 23,

the first circuit board is arranged parallel to the second circuit board and/or the friction disk is connected to the magnet body and to the first housing part, the first circuit board being pressed against the first housing part by the friction disk, the second circuit board being arranged axially between the first circuit board and the first housing part.

25. The drive of claim 22, wherein the drive is a linear drive,

it is characterized in that the preparation method is characterized in that,

a sensor for detecting wear of the brake lining is arranged in a housing formed by the first housing part and the second housing part,

the sensor wires are guided through the cable feed-throughs.

26. The drive device according to any one of claims 1 to 5,

it is characterized in that the preparation method is characterized in that,

an annular gap is provided between the first housing part and the shaft,

the axial length of the annular gap is greater than the radius of the annular gap,

the annular gap is arranged on the side of the first bearing facing away from the magnet body and/or the second bearing in the axial direction.

27. The drive device according to any one of claims 1 to 5,

it is characterized in that the preparation method is characterized in that,

the second bearing is designed as a double bearing.

28. A drive arrangement according to claim 27 wherein the second bearing comprises at least a cylindrical roller bearing.

29. The drive of claim 26,

a further annular gap is provided between the second housing part and the shaft,

the axial length of the further annular gap is greater than the radius of the further annular gap,

the second bearing is arranged on the side of the further annular gap facing away from the magnet body and/or the first bearing in the axial direction.

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