CN116201825A - Driving device - Google Patents

Abstract

The invention relates to a drive device having a shaft, a coupling part and a shaft sealing ring, wherein the coupling part has axially protruding claws which protrude at least partially into recesses of the shaft, which recesses are spaced apart from one another in the circumferential direction, which recesses are surrounded in the radial direction by an annular region of the shaft, the outer surface of which is finished to a cylindrical shape and/or which serves as a running surface for a sealing lip of the shaft sealing ring.

Description

Driving device

Technical Field

The invention relates to a drive device having a gear unit, which has a gear unit housing, a brake device that can be actuated electromagnetically, and a motor.

Background

It is generally known that the drive can be formed by a reduction gear driven by an electric motor.

Disclosure of Invention

The object of the invention is therefore to achieve a drive device that is explosion-proof and compact.

According to the invention, this object is achieved by a drive device according to the features given in claim 1.

An important feature of the invention in a drive is that the drive has a shaft, a coupling and a shaft sealing ring,

in particular, wherein the shaft is connected to the coupling in a rotationally fixed manner,

wherein the coupling has an axially projecting claw which projects at least partially into a recess of the shaft, in particular a recess introduced from the end side,

wherein the recesses are spaced apart from each other in the circumferential direction, in particular by a material region, in particular an inner jaw, which is formed on the shaft,

wherein the recess is circumferentially surrounded by an annular region of the shaft,

in particular, wherein the annular region delimits a recess radially outside,

wherein the outer, in particular radially outer, surface of the annular region is finished, in particular ground to a cylindrical shape, and/or the outer, in particular radially outer, surface of the annular region serves as a running surface for a sealing lip of the shaft sealing ring.

This has the advantage that no additional axial structural length needs to be provided for the shaft sealing ring. The jaws of the coupling extend into the corresponding recesses of the shaft.

In an advantageous embodiment, the drive device has a damping ring with an annular base body and a radially extending and/or shaped radiation region which protrudes into the recess and/or is arranged between the material region of the shaft, in particular the inner jaw, and the jaw of the shaft,

in particular, the wall thickness of the radiation area, measured in the circumferential direction, has a local maximum with increasing radial distance from the axis of rotation of the shaft,

in particular, wherein the respective claw portion is concavely shaped on its side contacting the respective radiation area, the respective material area is concavely shaped on its side contacting the respective radiation area,

in particular, wherein the radiation areas are regularly and/or uniformly spaced apart from each other in the circumferential direction,

in particular, wherein the material areas, in particular the inner claws, are regularly and/or uniformly spaced apart from one another in the circumferential direction,

in particular, the claw portions are regularly and/or uniformly spaced apart from one another in the circumferential direction.

In an advantageous embodiment, the drive device has a gear box with a gear box housing, an electromagnetically actuated brake device and an electric motor,

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

wherein the first housing part of the brake device receives the shaft sealing ring and the first bearing, the second housing part of the brake device receives the second bearing,

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

in which the shaft is connected in a rotationally fixed manner to a toothed part of the reduction gear, in particular to a toothed part of the first gear stage of the reduction gear, in particular to a pinion, or is embodied in one piece, in particular in one piece,

the rotor shaft of the electric machine is connected to the coupling element in a rotationally fixed manner, in particular, the rotor shaft protrudes into a bore of the coupling element and is connected to the coupling element in a form-locking manner in the circumferential direction by means of a key connection.

In an advantageous embodiment, the shaft protrudes through the magnet body of the brake device, in particular through the ferromagnetic coil body,

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,

in particular, the brake lining carrier is arranged to be movable relative to the shaft, in particular 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 persons who are not specially trained. In particular, the brake device is encapsulated in a burst-pressure-resistant/explosion-proof manner and thus only permits opening by specially trained personnel. However, the entire brake device can be removed from the drive device and replaced by another brake device by a person who is not specially trained.

Thus, maintenance at a low cost can be performed. In addition, the person is also authorized to maintain the motor and the retarder, i.e. in particular also to open the retarder and to refuel or replace the toothed part of the retarder.

Furthermore, the brake device itself may be equipped with wear sensors so that maintenance or replacement may be scheduled in time. Furthermore, the angle sensor can be integrated into the brake system, thereby increasing the operational safety and thereby reducing the operating costs, in particular also by timely maintenance and protection against damage.

It is also important that the brake lining carrier is arranged to be movable and thereby to make the braking action substantially independent of the state of wear of the brake lining carrier. This is because slight wear can be compensated for by this movement. This also improves the operational safety.

Furthermore, it is also advantageous if the shaft sealing ring does not require additional axial installation space, but can be arranged in the axial region of the claw and/or the inner claw. This is achieved in that the recess is surrounded by an annular region, which is designed as a cylindrical circumferential surface radially outwards, so that it can serve as a running surface for the sealing lip of the shaft sealing ring.

In an advantageous embodiment, the first housing part is connected to the second housing part,

in particular, the region of the first housing part that is in contact with the second housing part extends longer in the axial direction than in the radial direction. The advantage here is that the brake can be arranged in a housing which is resistant to the explosion pressure. The brake is thereby arranged in an encapsulated manner and as a transportable unit between the motor and the reduction gear.

In an advantageous embodiment, the shaft is connected to the 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. Thereby, the coupling function can be integrated into the brake device. The braking device thus also serves as an adapter between the motor and the reduction gear, wherein the braking device for example balances and/or compensates for deviations of the rotational axis of the rotor shaft from the rotational axis of the shaft.

In an advantageous embodiment, the shaft has claw portions at its axial end region facing the rotor shaft, which claw portions are spaced apart from one another in the circumferential direction,

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

wherein the coupling has claw portions on its axial end regions facing the shaft, which claw portions are spaced apart from each other in the circumferential direction,

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

in particular, the radial distance region covered by the claw of the coupling element, with reference to the axis of rotation of the shaft, is also covered by the claw of the shaft. The advantage here is that tolerance compensation can be brought about by means of the coupling. That is, if the rotor shaft and the axis of rotation of the shaft are not precisely aligned with each other, the coupling causes transmission of torque and attenuates lateral moment. In addition, a plastic material, in particular a plastic material of a star-shaped plastic star-shaped part, can be arranged between the claw parts, 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 the driver is fitted over the shaft, the driver being connected to the shaft in a form-fitting manner in the circumferential direction and/or by means of a key connection,

the driver has external teeth, which mesh with the internal teeth of the brake lining carrier. The advantage here is that the brake lining carrier compensates for the wear of the brake lining by movement. Since the spring element presses the brake lining carrier via the armature plate correspondingly closer to the friction plate when the brake lining is thin and the coil is current-free. Thus, the operation safety is high. Furthermore, with sensors arranged on the brake, in particular micro switches or inductive proximity sensors, it is monitored whether the wear exceeds an allowable extent. In this way, the operational safety is also further improved.

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

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, in particular axially, between the magnet body and the brake lining carrier,

in particular, the magnet body and/or the armature plate are made of ferromagnetic material. The advantage here is that the operational safety is increased, since the brake automatically engages when the coil is not energized.

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

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

In an advantageous embodiment, 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 formed as a prefabricated unit. The advantage here is that the brake can be assembled already before being installed in the housing of the brake device and can be stored as a functional unit in a warehouse and can then be installed in the housing. During assembly, the friction plate is connected to a first housing part of the housing of the brake device by means of a threaded element. The circuit board is preferably clamped between the friction plate and the first housing part.

In one advantageous embodiment, the magnet body, the coil, the spring element, the armature plate, the brake lining carrier, the friction plate and the pin are surrounded 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 is a magnet body, a coil, a spring element, an armature plate, a brake lining carrier, a friction plate forming a housing. The advantage here is that the brake can be assembled already before being installed in the housing of the brake device and can be stored as a functional unit in a warehouse and can then be installed in the housing. During assembly, the friction plate is connected to a first housing part of the housing of the brake device by means of a threaded element. The circuit board is preferably clamped between the friction plate and the first housing part.

In an advantageous embodiment, the rotary part is mounted so as to be rotatable 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 magnet body against the spring force generated by the spring element, and in a second rotational position of the rotor, the armature plate is movable in the axial direction, i.e. in the direction of the rotational axis of the shaft, in such a way that, in particular when the coil is not energized, the armature plate presses the brake lining carrier against the friction plate,

in particular, the rotary part is connected to the clamping band, in particular, the clamping band extends at least in sections, in particular with reference to the axis of rotation of the shaft, tangentially and/or circumferentially. The advantage here is that a manual release/release of the brake, i.e. a release that can be activated by hand, can be achieved. For this purpose, the clamping band is pivoted and the rotary part is thereby rotated in such a way that: so that the eccentric portion of the rotor presses the armature plate against the magnet body, in particular against the spring force generated by the spring element.

In an advantageous embodiment, the flange part is connected to the second housing part, and covers and/or in particular seals the opening of the gear housing in an oil-tight manner. The advantage here is that the entire housing of the brake device can be connected to the reduction gear via the flange element and held by the reduction gear. In particular, the motor can be fastened to the housing of the brake device and held by the housing. Furthermore, it is thereby also possible to connect the brake device to the retarder by persons without special training and then to add oil to the retarder. At this time, it is not necessary to open the brake enclosed in the housing of the brake device. The opening of the retarder can be covered with the flange element and thereby the retarder 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 reduction gear. Thus eliminating the need for flange members.

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

wherein the electrical conductors are guided through a cable feed-through of the explosion-proof pressure, which is arranged in the through recess of the first housing part. The advantage here is that the junction box itself is embodied to be resistant to explosion pressure. Thereby, the electrical connector may be provided on the electrical connection device and thus arranged in the area of the explosion-proof pressure. Furthermore, this region of the junction box is separated from the region of the brake and is connected only by a cable feed-through. Thus, the explosion cannot propagate from the region of the actuator to the region of the electrical connection device and vice versa. Thus, safety is improved.

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

wherein the other circuit board, namely the second circuit board, is connected with the shaft in a manner of being unable to rotate relatively,

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

in particular, the first printed circuit board is arranged parallel to the second printed circuit board and/or is pressed by the friction plate onto the first housing part, 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 circuit board is arranged in a clamping manner and can thus be connected in a cost-effective manner.

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

particularly wherein the sensor wire is led through the cable feed-through. 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,

wherein the annular gap is arranged on a side of the first bearing facing away from the magnet body and/or from the second bearing, in particular on a side of the first bearing facing away from the magnet body and/or from the second bearing in the axial direction. The advantage here is that the annular gap is embodied so narrow and so long in the axial direction that penetration of the explosion front (Explosionsfront) is prevented. Furthermore, the first bearing can be arranged in the region of the explosion-proof 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 embodied as a double bearing, in particular, wherein the second bearing has at least one cylindrical roller bearing. The advantage here is that, for example, the transverse forces occurring in the first gear stage can be guided out by means of the double bearing, and thus the annular gap arranged between the shaft and the second housing part does not change its thickness even in the event of a transverse force fluctuation, in particular the extent of its change cannot be detected.

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 from the first bearing, in particular on a side of the further annular gap facing away from the magnet body and/or from the first bearing in the axial direction. The advantage here is that the second bearing is accessible from the outside and can be replaced without having to open the housing of the brake device. Thus, the expertise of the professional is not required. The further annular gap does not change its thickness even in the event of a transverse force fluctuation, and in particular the extent of its change cannot be detected.

Further advantages result from the dependent claims. The invention is not limited to the combination of features of the claims. Other reasonable combinations of the claims and/or individual claim features and/or the description features and/or the drawing features will occur to those skilled in the art, especially from the objectives and/or the objectives presented in comparison with the prior art.

Drawings

The invention will now be explained in detail with reference to the schematic drawings:

fig. 1 shows a cross-sectional view of a brake device according to the invention.

Fig. 2 shows an oblique view of the brake device of fig. 1 in section.

Fig. 3 shows a cross-sectional view of another brake device.

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

Fig. 5 shows in an exploded manner the claw coupling formed by the coupling 10 and the shaft 2 connected thereto.

List of reference numerals:

1 flange member

2-axis

3 magnet body

4 coil

5 armature plate

6 brake lining support

7 friction plate

8 first housing part

9 first bearing

10 connector

12 first circuit board

13 permanent magnet

14 cable pipe

15 lower part

16 electric connection device

17 cover part

19 second housing part

20 second bearing

21 clamp

22 rotating member

23 driver

30 spring element

40 bearing seat

41 support rib

50 sealing surface

51 bearing block for the inner ring of the first bearing 9

52 vibration damping ring

Detailed Description

As shown in the figures, the braking device according to the invention is embodied as resistant to explosion pressure.

The brake device may be arranged between the motor and the reduction gear, wherein the brake device is held by the reduction gear housing. The rotor shaft of the motor can be connected in a rotationally fixed manner to the coupling element 10.

For example, the coupling element 10 is embodied as a sleeve which is fitted over a rotor shaft, not shown in the figures, and is connected in a rotationally fixed manner to the rotor shaft, 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 reduction gear, in particular to a toothed part of the first gear stage of the reduction gear.

For this purpose, the shaft 2 has a key slot, so that a sleeve pinion can be fitted onto the shaft 2 and connected to the latter in a rotationally fixed manner by means of a key. The nested pinion has external teeth and serves as the input toothed member of the first gear stage of the reduction gear.

The shaft 2 has, at its axial end facing away from the reduction gear and/or the toothed component, a claw which is operatively connected with a claw formed on the coupling 10 to form a claw coupling. For this purpose, the jaws of the shaft 2 are spaced apart from one another in the circumferential direction, in particular regularly, and project into the gap created by the circumferentially embodied spacing of the jaws of the coupling 10. In this way, the shaft 2 is connected in a form-locking manner in the circumferential direction to the coupling 10.

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

The flange part 1 is connected to the second housing part 19 and serves for connection to a reduction gear. 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 particular 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 motor. Thereby, the motor is held on the decelerator by the braking device.

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

The shaft sealing ring received in the second housing part 19 seals against the shaft 2.

The sleeve-shaped driver 23 is fitted over the shaft 2 and is connected in a rotationally fixed manner to the shaft 2, in particular by means of a key connection. On the radial outer circumference of the driver, the driver has an external toothing, onto which the brake lining carrier 6 is pushed, wherein the internal toothing of the brake lining carrier 6 engages, in particular, such that the brake lining carrier 6 is connected to the driver 23 in a rotationally fixed manner 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 with the axis of rotation 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 rotational axis of the shaft 2.

The armature plate 5 is preferably composed of ferromagnetic material. The armature plate 5 is connected to the magnet body 3 in a rotationally fixed manner, however the armature plate 5 is arranged to be movable in the axial direction, i.e. in the direction of the rotational axis of the shaft 2. For this purpose, pins are preferably inserted or screwed into axially oriented bores of the magnet body 3, which pins are guided through corresponding openings 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 against 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 the spring force generated by the spring element 30. In this case, the brake lining carrier 6 is pressed by the armature plate 5 against a braking surface formed on the friction plate 7. The friction plate 7 is connected, in particular fixedly connected, to the first housing part 8.

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

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

This configuration allows the components associated with the braking function to be prefabricated or preassembled and then inserted into the housing of the braking device.

To achieve prefabrication or preassembly, the material is to be assembled from

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

-an armature plate, which is arranged to be fixed to the housing,

-a pin guiding the armature plate

Brake lining carrier

The stack formed is formed as a prefabricated or preassembled brake by means of the connection of the friction plates 7. Subsequently, the brake is mounted in the housing by connecting the friction plate 7 with the first housing part 8. The friction plate is preferably connected to the magnet body 3 by means of pins, wherein the pins are inserted into holes in the magnet body. The friction plate 7 is screwed onto the pin, for example by means of a screw. Preferably, the pin is axially oriented.

When the brake is mounted in the housing of the brake device, the friction plate 7 is connected to the first housing part 8 by means of a screw element, wherein the screw element 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 disk 7 has a circumferential, annular recess in which permanent magnets 13 arranged directly on the friction disk 7 or on the first circuit board 12 can be accommodated.

The first circuit board 12 is held by the friction plate 7 in such a way as to press onto the first housing part 8.

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

The other circuit board is connected to the shaft 2 in a manner that it cannot rotate relative thereto. Thereby, the further circuit board is arranged rotatable with respect to the first circuit board 12.

By means of the functional connection with the permanent magnet, a sensor is realized by means of the circuit board, whereby the angular position of the shaft 2 can be detected by the sensor.

The first circuit board 12 and/or the further circuit board is 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.

However, other operating principles are also conceivable which do not require permanent magnets.

In any case, however, the first circuit board is arranged such that it cannot rotate relative to the first housing part 8 and the shaft 2 is connected to the further circuit board in a rotationally fixed manner.

The sensor signals are led from the first circuit board 12 into a junction box, which is arranged on the outside of the first housing part 8, by means of a cable through a cable feed-through 14 of the explosion-proof pressure. The junction box is formed by an annular lower part 15 seated on the first housing part and a cover 17 placed on the lower part. An electrical connection device 16 is arranged in the junction box, which forms a housing for the electrical connection device 16.

The junction box itself is thus also constructed to be resistant to explosion pressure.

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

Furthermore, a seal, in particular a planar 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, a gap region is formed which is as long as possible and as thin as possible in the contact region, so that a possible blast wave loses so much energy when passing through the gap region that it is prevented from propagating through the gap region.

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

Between the claw portions of the shaft 2 and the claw portions of the coupling member 10 in the circumferential direction, a radial region of the plastic star is arranged, so that fluctuation in the rotational speed can be suppressed.

Between the first housing part 8 and the second housing part 19 connected thereto, a gap region is formed in the contact region which is as long as possible and as thin as possible, so that a possible blast wave loses so much energy when passing through the gap region that it is prevented from propagating through the gap region. For this purpose, the extension of the gap region in the axial direction is at least four times greater than the extension in the radial direction, wherein the axial direction is parallel to the direction of the axis of rotation of the shaft 2.

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

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

The second bearing 20 is preferably embodied as a ball bearing, which is also assigned a cylindrical roller bearing or an angular bearing. The double bearing of the shaft 2 thus formed ensures that the orientation of the shaft 2 is as unchanged as possible, in particular when significant transverse moments are introduced into the shaft 2 by the sleeved pinion. This is particularly important because a very narrow but axially long annular gap exists between the shaft 2 and the second housing part 19, so that propagation of an explosion through this gap region is prevented. For this purpose, the annular gap preferably extends at least 50 times wider in the axial direction than in the radial direction.

Likewise, there is also such a narrow annular gap 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 bearing and thus the second bearing 20 are arranged on the side of the second housing part 19 facing away from the magnet body 3. In this way, the housing is connected after the brake has been installed in the housing of the brake device and is not opened thereafter by insufficiently trained personnel. Of course, this allows a person to connect the housing with the flange part 1 and to connect the flange part 1 to the gear housing very simply, and to replace the double bearing in advance during maintenance, even in particular without having to open the housing of the brake device.

In addition, a microswitch for monitoring the wear of the brake linings is arranged in the housing of the brake device. By means of the microswitch it is possible to monitor whether the distance of the coil 4 from the armature plate 5 in the engaged state of the brake, i.e. in the state in which the coil 4 is currentless, is below a threshold value. Thus, an alarm signal can be generated by the microswitch when the wear of the brake lining exceeds a threshold value. However, other distance sensors may be used instead of the micro-switch.

As shown in fig. 2, manual release of the brake can be achieved. For this purpose, the clamping band 21 is fastened to a rotatably mounted rotor 22, the rotor 22 having a non-circular, in particular eccentric, section. The pivoting of the collar 21 thus enables the pivoting element 22 to pivot, in particular about a pivot axis which is oriented perpendicular to the pivot axis of the shaft 2. As a result of this pivoting movement, the eccentric region is pressed against the armature plate 5, so that the armature plate 5 is pressed against the magnet body 3 and the brake is thereby released.

However, as shown in fig. 3, the opening of the gear housing can also be covered and the gear can be sealed in an oil-tight manner from the outside environment without the flange part 1 by connecting the second housing part 19 to the gear housing. For this purpose, in fig. 3, the second housing part 19 has a correspondingly shaped flange section facing a reduction gear unit, which is not shown in fig. 3. However, unlike the embodiment according to fig. 2, the double bearing can also be replaced by a correspondingly sized and stable single bearing, which has the disadvantage that the wall thickness of the second housing part 19 must be made smaller.

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 bearing ribs 41.

As shown in fig. 1 and 3, a shaft sealing ring is accommodated in the first housing part 8, which seals against the shaft 2. The sealing lip of the shaft sealing ring is in this case operated on a sealing surface 50, which adjoins a finished surface which also has a seat for the inner ring of the first bearing 9.

As shown in fig. 5, the coupling part 10 connected to the rotor shaft of the electric machine has axially projecting claw parts on its side facing the shaft 2, which claw parts project into recesses machined into the shaft 2 in the axial direction. The recesses are spaced apart from one another in the circumferential direction, in particular regularly and/or uniformly.

The shaft 2 has radially inwardly projecting jaws, i.e. inner jaws. Corresponding recesses are arranged between the respective inner claws in the circumferential direction. The recesses are open towards the coupling 10 so that the jaws of the coupling protrude into the recesses.

The recesses are delimited radially outside by an annular region of the shaft 2, which is preferably embodied as hollow-cylindrical in the circumferential corner region covered by the recesses. The outer surface of the annular region of the shaft 2 is finished and can thus serve as a sealing surface. The sealing lip of the shaft sealing ring received in the first housing part 8 thereby contacts the shaft 2 on this sealing surface 50.

In order to suppress torque fluctuations, a damping ring 52 is arranged between the shaft 2 and the coupling 10. The damping ring has an annular base region and radially extending, in particular radially outwardly extending, radiation regions formed on the base region, which are arranged in particular regularly and/or uniformly with respect to one another in the circumferential direction.

The radial region has a wall thickness measured in the circumferential direction, which increases first and then decreases with increasing radial distance from the axis of rotation of the shaft. Thus, the wall thickness has a local maximum as a function of radial distance. The shape of the bulge thus created improves the suppression of torque ripple.

The advantage of the invention is thus that the area covered by the inner jaw in the axial direction comprises the area covered by the sealing lip in the axial direction and/or the area covered by the sealing surface 50 in the axial direction.

A very compact axial solution is thereby achieved for the form-locking transmission of torque into the region of the explosion-proof pressure.

The bearing seat 51 for the inner ring of the first bearing 9 is finished and abuts the sealing surface 50. The length of the bearing block in the axial direction is such that the finished region has a very small distance between the shaft 2 and the first housing part 8, i.e. a very thin annular air gap. In this way, the explosion front arriving in the air gap cannot disadvantageously continue to propagate axially, but only with energy losses.

The first bearing 9 is seated on the inner side of the wall of the first housing part 8 and the shaft sealing ring is seated on the outer side of the wall of the first housing part 8 facing the motor.

In a further embodiment according to the invention, the first bearing 9 is also implemented as a double bearing.

Claims (15)

1. A drive device having a shaft, a coupling and a shaft seal ring,

in particular, wherein the shaft is connected to the coupling in a rotationally fixed manner,

the coupling has axially projecting claw parts which at least partially protrude into recesses of the shaft, in particular recesses which are introduced from the end side,

the recesses are spaced apart from one another in the circumferential direction, in particular by material regions which are formed on the shaft, in particular inner claws,

the recess is circumferentially surrounded by an annular region of the shaft,

in particular, wherein the annular region delimits the recess radially outside,

the outer, in particular radially outer, surface of the annular region is finished, in particular ground to a cylindrical shape, and/or the outer, in particular radially outer, surface of the annular region serves as a running surface for a sealing lip of the shaft sealing ring.

2. Drive device according to claim 1, characterized in that it has a damping ring with an annular base body and a radially extending radiation zone formed on the base body, which radiation zone protrudes into the recess and/or is arranged between a material zone of the shaft, in particular an inner jaw, and a jaw of the shaft,

in particular, the wall thickness of the radiation region, measured in the circumferential direction, has a local maximum with increasing radial distance from the axis of rotation of the shaft,

in particular, wherein the respective claw portion is concavely shaped on its side contacting the respective radiation area, the respective material area is concavely shaped on its side contacting the respective radiation area,

in particular, wherein the radiation areas are regularly and/or uniformly spaced apart from each other in the circumferential direction,

in particular, wherein the material regions, in particular the inner claws, are regularly and/or uniformly spaced apart from one another in the circumferential direction,

in particular, the claw portions are regularly and/or uniformly spaced apart from one another in the circumferential direction.

3. Drive device according to claim 1 or 2, characterized in that the drive device has a gear box with a gear box housing, an electromagnetically actuatable brake device and a motor,

the braking device is arranged between the decelerator and the motor,

a shaft sealing ring and a first bearing are 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,

the shaft is connected in a rotationally fixed manner to a toothed part of the reduction gear, in particular to a toothed part of the first gear stage of the reduction gear, in particular to a pinion gear, or is embodied in one piece, in particular in one piece,

the rotor shaft of the electric machine is connected to the coupling element in a rotationally fixed manner, in particular, wherein the rotor shaft protrudes into a bore of the coupling element and is connected to the coupling element in a form-fitting manner in the circumferential direction by means of a key connection.

4. Drive device according to any of the preceding claims, characterized in that the shaft protrudes through the magnet body of the brake device, in particular through a ferromagnetic coil body,

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,

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

5. A driving device according to claim 3 or 4, wherein the first housing part is connected to the second housing part,

in particular, the region of the first housing part which is in contact with the second housing part extends longer in the axial direction than in the radial direction,

and/or the shaft is connected in a rotationally fixed manner to the rotor shaft of the electric machine,

and/or the shaft has claw portions spaced apart from each other in the circumferential direction on an axial end region thereof facing the rotor shaft,

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

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

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

in particular, the radial distance region covered by the claw of the coupling element, with reference to the axis of rotation of the shaft, is also covered by the claw of the shaft.

6. Drive device according to one of the preceding claims, wherein the brake lining carrier is arranged to be axially movable relative to the shaft, in particular wherein a driver is fitted over the shaft, which driver is connected to the shaft in a form-fitting manner in the circumferential direction and/or by means of a key connection,

the driver has external teeth which mesh with internal teeth of the brake lining carrier.

7. Drive device according to any of the preceding claims, wherein the armature plate is connected to the magnet body in a rotationally fixed and axially movable manner,

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

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

in particular, the magnet body and/or the armature plate are made of ferromagnetic material.

8. Drive device according to any of the preceding claims, characterized in that the friction plate is connected to the magnet body, in particular by means of a pin which protrudes into the magnet body and guides the armature plate,

in particular, the friction plate is connected to the first housing part.

9. A drive arrangement according to any one of the preceding claims, 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 constructed as a prefabricated unit, and/or

The magnet body, coil, spring element, armature plate, brake lining carrier, friction plate and pin are surrounded 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 is a housing formed by the magnet body, coil, spring element, armature plate, brake lining carrier, friction plate and pin.

10. Drive device according to any of the preceding claims, wherein the rotation element is rotatably supported relative to the first housing part, in particular about a rotation axis oriented perpendicularly to the rotation axis of the shaft,

the rotating member has an eccentric area and,

in a first rotational position of the rotor, the eccentric region presses the armature plate against the magnet body against the spring force generated by the spring element, 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, in particular when the coil is not energized, the armature plate presses the brake lining carrier against the friction plate,

in particular, the rotary part is connected to the clamping band, in particular, the clamping band extends at least in sections, in particular with reference to the axis of rotation of the shaft, tangentially and/or circumferentially.

11. Drive device according to any of the preceding claims, characterized in that a flange part is connected to the second housing part, which flange part covers and/or in particular closes the opening of the gear housing in an oil-tight manner.

12. Drive arrangement according to any of the preceding claims, characterized in that a lower part is connected on the outside of the first housing part, on which lower part a cover part is placed, whereby an electrical connection device is arranged in a junction box formed by the lower part and the cover part, which junction box forms a housing for the electrical connection device,

the electrical conductors are guided through a cable feed-through of the explosion-proof pressure, which is arranged in the through recess of the first housing part.

13. Drive device according to any of the preceding claims, wherein the first circuit board is connected to the first housing part in a rotationally fixed manner,

the other circuit board, namely the second circuit board, is connected to the shaft in a manner not to rotate relative thereto,

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

in particular, the first printed circuit board is arranged parallel to the second printed circuit board and/or is pressed by the friction plate onto the first housing part, in particular, the second printed circuit board is arranged axially between the first printed circuit board and the first housing part.

14. Drive device according to any of the preceding claims, characterized in that the sensor for detecting wear of the brake lining is arranged in a housing formed by a first housing part and a second housing part,

particularly wherein the sensor wire is led through the cable feed-through.

15. Drive device according to any of the preceding claims, wherein 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 a side of the first bearing facing away from the magnet body and/or from the second bearing, in particular on a side of the first bearing facing away from the magnet body and/or from the second bearing in the axial direction,

and/or

The second bearing is embodied as a double bearing, in particular wherein the second bearing has at least one cylindrical roller bearing,

and/or

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,

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

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