DRIVE, HAVING A GEARBOX WITH A GEARBOX HOUSING, AN ELECTROMAGNETICALLY ACTUATED BRAKE ARRANGEMENT AND AN ELECTRIC MOTOR

Description

[0001] The invention relates to a drive comprising a transmission with a transmission housing, an electromagnetically actuated brake arrangement and an electric motor.

[0002] It is generally known that a drive can be formed by a transmission driven by an electric motor.

[0003] From EP 2 677 197 A1, a transmission is known as the closest prior art.

[0004] An electromagnetically actuated brake is known from DE 10 2014 018 485 B3.

[0005] An electromagnetically actuated brake arrangement is known from US 2021 / 0 131 512 A1.

[0006] A hermetically sealed entry for a cable harness is known from DE 79 28 392 U1.

[0007] An electric motor is known from DE 10 2010 049 748 A1.

[0008] DE 10 2010 049 747 A1 discloses a kit for producing different electric motors.

[0009] A brake is known from DE 10 2010 0449 744 A1.

[0010] An adapter for a drive is known from DE 10 2019 003 545 A1.

[0011] A drive with adapter is known from DE 10 2019 003 546 A1.

[0012] From the US 6 328 655 B1 The closest state of the art is an adapter system.

[0013] From the US 2019 / 296504 A1 a connection arrangement is known.

[0014] From the EP 1 549 546 A1 A system for observing a liquid level is known.

[0015] The invention is therefore based on the object of achieving increased safety in a drive.

[0016] According to the invention, the object is achieved by the drive according to the features specified in claim 1.

[0017] Important features of the drive are that the drive comprises a gearbox with a gearbox housing, an electromagnetically actuated brake arrangement and an electric motor, wherein the brake arrangement is arranged between the gearbox and the electric motor, wherein a first bearing is accommodated in a first housing part of the brake assembly and a second bearing is accommodated in a second housing part of the brake assembly, wherein a shaft is rotatably mounted by means of the first and second bearings, wherein the shaft is rotationally fixedly connected to a toothed part of the transmission, in particular to a toothed part, in particular a slip-on pinion, of the first gear stage of the transmission, or is designed in one piece, in particular in one piece, with this toothed part, wherein the shaft projects through a magnetic body, in particular through a ferromagnetic coil body, of the brake assembly, wherein the shaft is rotationally fixedly connected to a brake pad carrier, which is arranged in the axial direction between the first and the second bearing, wherein a cable feedthrough is arranged in the first housing part, which has a screw nut and a sealing element,wherein the sealing element is inserted into a stepped bore and the screw nut is screwed into a threaded bore of the first housing part, wherein the threaded bore is aligned coaxially to the stepped bore, wherein the screw nut bears against the sealing element, in particular wherein the sealing element is made of rubber or plastic, wherein the brake pad carrier is arranged displaceably relative to the shaft, in particular parallel to the axis of rotation of the shaft.

[0018] The advantage here is that increased safety can be achieved. For this purpose, a sealing element is provided which is inserted into a stepped bore and is subjected to force by a screw nut. This makes the sealing element elastically deformable so that the sealing element rests tightly on the wall of the stepped bore on its outer circumference and also tightly on the cables and pins passing through the sealing element. This way, an explosion-pressure-resistant cable feedthrough can be achieved. The cables from the coil and the sensor(s) of the brake assembly can be led through the wall of the second housing part into the interior of a junction box, whereby this interior is hermetically separated from the interior of the brake assembly containing the brake. In particular, manual release of the brake is also possible from the outside through the second housing part by means of a rotating part.This enables safe operation even in potentially explosive environments.

[0019] "Explosion-resistant" here means that the cable entry can withstand an overpressure of at least 3 bar, especially during an explosion. The maximum pressure for the cable entry is therefore preferably 3 bar.

[0020] According to the invention The sealing element has continuous recesses through which either a cable is passed or a pin protrudes. The recesses are each aligned parallel to the axis of the cylindrical bore, with one of the recesses having a larger inner diameter than another. The advantage here is that none of the recesses is empty. This ensures a high level of tightness.

[0021] In an advantageous embodiment, each of the recesses has at least one constriction, which is deformed by the respective cable or by the respective pin. This is advantageous in that improved sealing can be achieved because the pin is connected with a force fit.

[0022] In an advantageous embodiment, the sealing element is barrel-shaped and / or has at least one convex, particularly barrel-shaped, surface area. This is advantageous in that elastic deformation can be achieved as soon as it is inserted into the recess. Thus, sealing is achieved immediately upon insertion.

[0023] In an advantageous embodiment, the sealing element is positioned against a step of the stepped bore. The diameter of the sealing element is advantageously larger than the clear inner diameter at the step of the stepped bore. Thus, the screw bushing presses the sealing element against the step, deforming it in such a way that a high degree of tightness is achieved with respect to the first housing, meaning that the cables and pins are sealed against the first housing part.

[0024] In an advantageous embodiment, the drive comprises a transmission with a transmission housing, an electromagnetically actuated brake arrangement and an electric motor, wherein the brake arrangement is arranged between the transmission and the electric motor, wherein a first bearing is accommodated in a first housing part of the brake assembly and a second bearing is accommodated in a second housing part of the brake assembly, wherein a shaft is rotatably mounted by means of the first and second bearings, wherein the shaft is non-rotatably connected to a toothed part of the transmission, in particular to a toothed part, in particular a slip-on pinion, of the first gear stage of the transmission, or is designed in one piece, in particular in one piece, with this toothed part, wherein the shaft projects through a magnetic body, in particular through a ferromagnetic coil body, of the brake assembly, wherein the shaft is non-rotatably connected to a brake pad carrier, which is arranged in the axial direction between the first and the second bearing, wherein a rotating part is rotatably mounted relative to the first housing part, in particular about a rotational axis that is oriented perpendicular to the rotational axis of the shaft,wherein a screw bushing is screwed with its external thread into a threaded bore passing through the first housing part and a rotating part is received in the screw bushing and rotatably mounted, wherein the rotating part protrudes from the screw bushing on both sides, wherein the rotating part has an eccentric region which is in operative connection with an armature disk of the brake arrangement, in particular for manually actuated release of the brake arrangement, in particular wherein the brake pad carrier is arranged displaceably relative to the shaft, in particular parallel to the axis of rotation of the shaft.

[0025] The advantage here is that the rotating part is received in the screw bushing in such a way that a cylindrical region is received in an inner cylindrical recess of the screw bushing and rests in such a way that the brake assembly is explosion-pressure-resistant, in particular and an explosion front cannot propagate between the screw bushing and the rotating part. This enables manually operated rotation of the rotating part by pivoting the bracket, thereby rotating the rotating part in the screw bushing, so that the non-circular section, in particular the region, of the rotating part releases the armature disk of the brake assembly against the spring force generated by spring elements of the brake assembly and acting on the armature disk of the brake assembly, i.e., pushes it away from the brake pad carrier.

[0026] In an advantageous embodiment, the screw bushing is made of a softer material than the turned part, In particular, the rotating part is made of hardened steel and the screw part is made of a material containing copper, in particular a copper alloy and / or brass. The advantage here is that the rotating part is mounted on a plain bearing and thus has minimal bearing clearance. Furthermore, copper is a very good thermal conductor, so that an explosion front attempting to spread between the screw bushing and the rotating part loses heat very quickly, and the spread can thus be prevented even more quickly than with the use of less thermally conductive materials.

[0027] In an advantageous embodiment, the rotary part has a collar region, in particular a collar region which is continuously circumferential relative to the axis of rotation of the rotary part, wherein the collar region abuts the screw part, in particular wherein the collar region protrudes radially from the rotating part relative to the rotational axis of the rotating part, and / or wherein the collar region is arranged axially between the non-circular region and the round, in particular cylindrical, section, in particular region, of the rotating part. The advantage here is that axial limitation and / or positioning is made possible in a simple manner.

[0028] In an advantageous embodiment, the rotating part has a non-circular dome area that protrudes into a recess in a bracket, particularly for the rotationally fixed connection of the bracket to the rotating part. This is advantageous because a rotationally fixed connection between the bracket and the rotating part can be easily achieved.

[0029] In an advantageous embodiment, a return spring supported on the first housing part is connected to the bracket, in particular wherein the return spring comprises a spiral spring and / or is made of a wire whose first end is bent and / or inserted into a recess in the bracket and whose second end is inserted into a housing part. This is advantageous in that the bracket can be easily reset, thus automatically ending the manually initiated ventilation when the manual operation is completed.

[0030] In an advantageous embodiment, the drive comprises a gear unit with a gear housing, an electromagnetically actuated brake arrangement and an electric motor, wherein the brake arrangement is arranged between the gear unit and the electric motor, wherein a first bearing is accommodated in a first housing part of the brake arrangement and a second bearing is accommodated in a second housing part of the brake arrangement, wherein a shaft is rotatably mounted by means of the first and second bearings, wherein the shaft is connected in a rotationally fixed manner to a toothed part of the transmission, in particular to a toothed part, in particular a slip-on pinion, of the first gear stage of the transmission, or is designed in one piece, in particular in one piece, with this toothed part, wherein the shaft projects through a magnetic body, in particular through a ferromagnetic coil body, of the brake arrangement, wherein the shaft is connected in a rotationally fixed manner to a brake pad carrier which is arranged in the axial direction between the first and the second bearing, in particular wherein the brake pad carrier is arranged displaceably relative to the shaft, in particular parallel to the axis of rotation of the shaft.

[0031] The advantage is that operating costs are low because maintenance can be performed even by non-specially qualified personnel. In particular, the brake assembly is encapsulated in an explosion-proof manner and may therefore only be opened by specially qualified personnel. However, the entire brake assembly can be removed from the drive by non-specially qualified personnel and replaced with another brake assembly.

[0032] This allows for cost-effective maintenance. Furthermore, this personnel is also authorized to service the electric motor and transmission, including opening the transmission and refilling oil or replacing gearing components.

[0033] Furthermore, the brake assembly itself can be equipped with a wear sensor, allowing for timely maintenance or replacement. An angle sensor can also be integrated into the brake assembly, increasing operational reliability and thus reducing operating costs, particularly through timely maintenance and damage prevention.

[0034] It's also important that the brake pad carrier is designed to be movable, so that the braking effect is essentially independent of the wear of the brake pads on the brake pad carrier. Minor wear can be compensated for by moving the brake pad carrier. This also increases operational reliability.

[0035] In an advantageous embodiment, the first housing part is connected to the second housing part, in particular, the area of contact between the first housing part and the second housing part is wider in the axial direction than in the radial direction. Advantageously, the brake can be provided in an explosion-proof housing. Thus, the brake is encapsulated and can be arranged as a portable unit between the motor and the transmission.

[0036] In an advantageous embodiment, the shaft is connected to the rotor shaft of the electric motor in a rotationally fixed manner. This is advantageous because the shaft can be connected to the rotor shaft via a coupling, in particular a claw coupling. This allows a coupling function to be integrated into the brake assembly. The brake assembly also functions as an adapter between the motor and the gearbox, for example, compensating for and / or offsetting deviations between the rotor shaft's axis of rotation and the shaft's axis of rotation.

[0037] In an advantageous embodiment, the shaft has claws spaced apart from one another in the circumferential direction at its axial end region facing the rotor shaft, wherein a coupling part is connected to the rotor shaft in a rotationally fixed manner, in particular by means of a keyway connection, wherein the coupling part has claws spaced apart from one another in the circumferential direction on its axial end region facing the shaft, wherein the region covered by the claws of the coupling part in the axial direction overlaps with the region covered by the claws of the shaft in the axial direction, in particular wherein the claws of the coupling part cover a radial distance range related to the axis of rotation of the shaft, which is also covered by the claws of the shaft. The advantage here is that tolerance compensation can be effected by means of the coupling, in particular by means of the coupling part. Therefore, if the axes of rotation of the rotor shaft and shaft are not exactly aligned with one another, the coupling, in particular the coupling part, transmits the torque and dampens transverse moments.In addition, plastic material, in particular a star-shaped plastic star, can be provided between the claws so that speed fluctuations are dampened.

[0038] In an advantageous embodiment, the brake pad carrier is arranged so as to be axially movable relative to the shaft, in particular wherein a driver is slipped onto the shaft, which is positively connected to the shaft in the circumferential direction and / or which is positively connected to the shaft by means of a keyway, wherein the driver has external teeth which engage with the internal teeth of the brake pad carrier. The advantage here is that the brake pad carrier initially compensates for wear on the brake pads through this movement. With thinner brake pads and a de-energized coil, the spring elements press the brake pad carrier closer to the friction disc via the armature disk. This ensures high operational reliability. In addition, wear is monitored for exceeding a permissible level using a sensor arranged on the brake, in particular a microswitch or inductive proximity sensor.This also further increases operational safety.

[0039] In an advantageous embodiment, an armature disk is connected to the magnetic body in a rotationally fixed manner and is axially movable, wherein spring elements supported on the magnetic body press against the armature disk, in particular applying spring force to the armature disk. The armature disk is arranged between, in particular axially between, the magnetic body and the brake pad carrier, in particular wherein the magnetic body and / or the armature disk are made of ferromagnetic material. The advantage here is that operational reliability is increased, since the brake is automatically applied when the coil is de-energized.

[0040] In an advantageous embodiment, a friction disc is connected to the magnetic body, in particular by means of bolts that extend into the magnetic body and guide the armature disc, in particular with the friction disc being connected to the first housing part. This is advantageous because the brake can be pre-assembled, thus increasing safety.

[0041] In an advantageous embodiment, the brake, comprising the magnet body, the coil, the spring elements, the armature disk, the brake pad carrier, the friction disk, and the bolts, is pre-assembled. This is advantageous in that the brake can be assembled before installation in the housing of the brake assembly and stored as a functional unit in a warehouse before being installed in the housing. During installation, the friction disk is connected to the first housing part of the brake assembly housing by means of screws. Preferably, a circuit board is clamped between the friction disk and the first housing part.

[0042] In an advantageous embodiment, the magnetic body, the coil, the spring elements, the armature disk, the brake pad carrier, the friction disk, and the bolts are surrounded and / or enclosed by the housing formed from the first and second housing parts. This is advantageous in that the brake can be assembled before installation in the housing of the brake assembly and stored as a functional unit in a warehouse before being installed in the housing. During installation, the friction disk is connected to the first housing part of the housing of the brake assembly using screws. Preferably, a circuit board is clamped between the friction disk and the first housing part.

[0043] In an advantageous embodiment, a rotating part is mounted rotatably relative to the first housing part, in particular about an axis of rotation which is aligned perpendicular to the axis of rotation of the shaft, wherein the rotating part has an eccentric region, wherein in a first rotational position of the rotating part the eccentric region presses the armature disk towards the magnetic body against the spring force generated by the spring elements, and in a second rotational position of the rotating part the armature disk is movable in the axial direction, i.e. in the direction of the axis of rotation of the shaft, such that the armature disk presses the brake pad carrier onto the friction disk, in particular when the coil is de-energized, in particular wherein the rotating part is connected to a retaining bracket, in particular wherein the retaining bracket extends at least in sections, in particular with respect to the axis of rotation of the shaft, tangentially and / or in the circumferential direction. The advantage here is that manual release, i.e. manually activated brake release, is achievable.For this purpose, a retaining bracket is pivoted and the rotating part is rotated in such a way that the eccentric part of the rotating part presses the armature disk towards the magnet body, in particular against the spring force generated by the spring elements.

[0044] In an advantageous embodiment, a flange part is connected to the second housing part, which covers an opening in the gearbox housing and / or closes it in an oil-tight manner. This is advantageous in that the brake assembly, with its entire housing, can be connected to the gearbox via the flange part and is held in place by the gearbox. In particular, the motor can be fastened to the housing of the brake assembly and is held in place by this housing. Furthermore, this means that even non-specially qualified personnel can be used to connect the brake assembly to the gearbox and then fill the gearbox with oil. The brake encapsulated in the housing of the brake assembly does not have to be opened. The opening in the gearbox can be covered with the flange part, and thus the gearbox can then be filled with oil. In a further development, the second housing part of the brake assembly can even be used directly to cover the opening in the gearbox. A flange part is then unnecessary.

[0045] In an advantageous embodiment, a lower part is connected to the outside of the first housing part, onto which a cover is placed, so that electrical connection devices are arranged and housed in the connection box thus formed from the lower part and the cover, with electrical cables being routed through an explosion-proof cable bushing arranged in a continuous recess in the first housing part. An advantage here is that the connection box itself is designed to be explosion-proof. This means that the electrical connections can be provided on the connection devices and are therefore arranged in the explosion-proof area. Furthermore, this area of the connection box is separated from the brake area and is only connected via a cable bushing. This means that an explosion cannot spread from the brake area to the connection devices area and vice versa. This increases safety.

[0046] In an advantageous embodiment, a first circuit board is connected in a rotationally fixed manner to the first housing part, wherein a second, in particular further, printed circuit board is connected to the shaft in a rotationally fixed manner, wherein the first printed circuit board is equipped with electronic components such that the angular position of the second printed circuit board and / or of the shaft is detectable, in particular wherein the first printed circuit board is arranged parallel to the second printed circuit board and / or wherein the first printed circuit board is pressed against the first housing part by the friction disc, in particular wherein 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 clamped manner and can thus be connected cost-effectively.

[0047] In an advantageous embodiment, a sensor for detecting brake pad wear is arranged in the housing formed by the first and second housing parts, in particular with the sensor lines passing through the cable feedthrough. This is advantageous because maintenance can be carried out in a timely manner.

[0048] In an advantageous embodiment, an annular gap is arranged between the first housing part and the shaft, in particular, its axial length is greater than the radius of the annular gap, wherein the annular gap is arranged on the side of the first bearing facing away from the magnetic body and / or the second bearing, in particular on the side of the first bearing facing away from the magnetic body and / or the second bearing in the axial direction. The advantage here is that the annular gap is designed to be so narrow and axially long that penetration of an explosion front is prevented. Furthermore, the first bearing can be arranged in an explosion-pressure-resistant area, thus increasing operational reliability because the rotatability of the shaft is reliably ensured.

[0049] In an advantageous embodiment, the second bearing is designed as a double bearing, in particular, wherein the second bearing comprises at least one cylindrical roller bearing. This is advantageous because transverse forces, which arise, for example, in the first gear stage, can be dissipated via the double bearing, and thus the annular gap arranged between the shaft and the second housing part does not change its thickness, in particular, does not change measurably, even with fluctuating transverse forces.

[0050] In an advantageous embodiment, a further annular gap is arranged between the second housing part and the shaft, in particular its axial length is greater than the radius of the further annular gap, wherein the second bearing is arranged on the side of the further annular gap facing away from the magnetic body and / or the first bearing, in particular on the side of the further annular gap facing away from the magnetic 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 arrangement. This means that no special qualifications of a specialist are required. The further annular gap does not change its thickness, in particular not measurably, even with fluctuating transverse force.

[0051] Further advantages emerge from the dependent claims. The invention is not limited to the combination of features in the claims. Further possible combinations of claims and / or individual claim features and / or features of the description and / or the figures will become apparent to those skilled in the art, particularly from the problem and / or the problem posed by comparison with the prior art.

[0052] The invention will now be explained in more detail using schematic illustrations: In the Figure 1 a cross section through a brake arrangement according to the invention is shown. Figure 2 An oblique view of a cutaway representation of the brake assembly is shown. Figure 3 A cross-section of another brake arrangement is shown. Figure 4 An oblique view of the brake assembly is shown. Figure 5a cross-section of a portion of the brake assembly is shown enlarged, showing a rotating part 22. In the Figure 6 The rotating part 22 is shown in an oblique view. In the Figure 7 The cable entry 14 is shown in more detail in cross-section. Figure 8 Pins (74, 80) of the cable gland 14 are shown in an oblique view. Figure 9 A seal 70 of the cable gland 14 is shown in an oblique view. Figure 10 a nut 71 of the cable gland 14 is shown in an oblique view.

[0053] As shown in the figures, the brake arrangement according to the invention is designed to be explosion pressure resistant.

[0054] The brake assembly can be arranged between an electric motor and a transmission, with the brake assembly being held by the transmission housing. The rotor shaft of the electric motor can be connected in a rotationally fixed manner to a coupling part 10.

[0055] For example, the coupling part 10 is designed in a sleeve-like manner and is placed on the rotor shaft (not shown in the figures) and connected in a rotationally fixed manner, in particular by means of a key connection.

[0056] A shaft 2 of the brake arrangement is connected in a rotationally fixed manner to a toothed part of the transmission, in particular to a toothed part of the first gear stage of the transmission.

[0057] For this purpose, shaft 2 has a keyway so that a slip-on pinion can be slipped onto shaft 2 and connected to the shaft in a rotationally fixed manner by means of a key. The slip-on pinion has external teeth and functions as the input gearing of the first gear stage of the transmission.

[0058] At its axial end facing away from the transmission and / or gearing part, the shaft 2 has claws which, as a claw coupling, are operatively connected to claws formed on the coupling part 10. For this purpose, the claws of the shaft 2 are spaced apart from one another in the circumferential direction, in particular regularly, and extend into the spaces created by the circumferential spacing of the claws of the coupling part 10. In this way, the shaft 2 is positively connected to the coupling part 10 in the circumferential direction.

[0059] The shaft 2 is rotatably supported by means of a first bearing 9 accommodated in a first housing part 8 and by means of a bearing 20 accommodated in a second housing part 19.

[0060] A flange part 1 is connected to the second housing part 19 and serves to connect it to the gearbox. For this purpose, the flange part 1 is connected to the gearbox housing using screws.

[0061] When connecting the flange part 1 to the transmission housing, an opening in the transmission housing is sealed, particularly in an oil-tight manner. The flange part 1 holds the 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. Thus, the electric motor is held to the transmission via the brake assembly.

[0062] The pressure-resistant, explosion-proof design of the brake assembly housing ensures high stability and rigidity. Therefore, the brake assembly housing can support the weight of the electric motor.

[0063] A shaft seal ring accommodated in the second housing part 19 seals against shaft 2.

[0064] A sleeve-shaped driver 23 is mounted on the shaft 2 and connected in a rotationally fixed manner, in particular by means of a keyway. On its radially outer circumference, the driver has an external toothing, onto which a brake pad carrier 6 is pushed, with an internal toothing of the brake pad carrier 6 engaging the external toothing. In particular, the brake pad carrier 6 is thus connected in a rotationally fixed manner to the driver 23 and is axially displaceable relative to the driver 23.

[0065] In the second housing part 19, a magnetic body 3 is accommodated, which has an annular recess in which a coil, in particular a ring winding, is accommodated, in particular wherein the ring axis is aligned coaxially to the axis of rotation of the shaft 2.

[0066] An armature disk 5 is arranged in the axial direction, i.e. in the direction of the axis of rotation of the shaft 2, between the magnetic body 3 and the brake pad carrier 6.

[0067] The armature disk 5 is preferably made of ferromagnetic material. Although the armature disk 5 is non-rotatably connected to the magnetic body 3, the armature disk 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, bolts are preferably inserted or screwed into axially directed bores in the magnetic body 3, which extend through corresponding recesses in the armature disk 5.

[0068] The brake pad carrier 6 preferably has a brake pad on each axial side.

[0069] Spring elements 30 supported on the magnet body 3 press on the armature disk 5, so that the armature disk 5 is pressed toward the brake pad carrier 6 with the spring force generated by the spring elements 30 when the coil 4 is de-energized. The brake pad carrier 6 is pressed by the armature disk 5 toward a braking surface formed on a friction disk 7. The friction disk 7 is connected, in particular firmly connected, to the first housing part 8.

[0070] However, when the coil 4 is energized, the armature disk 5 is attracted to the magnetic body 3 against the spring force generated by the spring elements 30 and thus the brake is released.

[0071] The friction disc 7 is preferably designed in the shape of a rotary disc or substantially circular disc, so that the connection between the friction disc 7 and the first housing part 8 is uninterrupted around the entire circumference. The friction disc 7 is preferably firmly connected to the first housing part 8.

[0072] This design allows the elements related to the brake function to be pre-assembled and then installed in the housing of the brake assembly.

[0073] For pre-completed training, the the magnet body 3 including spring elements and coil 4 accommodated in it, the armature disc, the bolts guiding the armature disc and the brake pad carrier The stack formed is formed as a pre-assembled brake by connecting the friction disc 7. This brake is then installed in the housing by connecting the friction disc 7 to the first housing part 8. The friction disc is preferably connected to the magnet body 3 via the bolts, wherein the bolts are inserted into bores in the magnet body. The friction disc 7 is screwed to the bolts, for example, by means of screws. The bolts are preferably axially aligned.

[0074] When installing the brake in the housing of the brake assembly, the friction disc 7 is connected to the first housing part 8 by means of screws, wherein the screws are screwed into threaded holes of the first housing part 8.

[0075] On the side facing away from the brake pad carrier 6, the friction disc 7 has a circumferentially encircling, annular recess in which a permanent magnet 13 can be accommodated, which is arranged directly on the friction disc 7 or on the circuit board 12.

[0076] The circuit board 12 is held pressed against the first housing part 8 by the friction disc 7.

[0077] The permanent magnets can be arranged either separately or on the circuit board 12.

[0078] Another circuit board is connected to the shaft 2 in a rotationally fixed manner. Thus, the additional circuit board is arranged so that it can rotate relative to the first circuit board 12.

[0079] In operative connection with the permanent magnets, a sensor is realized by means of the circuit boards so that the angular position of the shaft 2 can be detected by the sensor.

[0080] The first circuit board 12 and / or the further circuit board is or are equipped with electronic components, so that a detector circuit is arranged on the first and / or further circuit board, which enables detection of the angular position of the shaft 2.

[0081] However, other operating principles can also be envisaged that do not require permanent magnets.

[0082] In any case, the first circuit board is arranged in a rotationally fixed manner to the first housing part 8 and the shaft 2 is connected in a rotationally fixed manner to the further circuit board.

[0083] From the first circuit board 12, the sensor signals are routed by a cable through an explosion-proof cable gland 14 into a terminal box located on the outside of the first housing part 8. This terminal box is formed by placing an annular lower part 15 and a cover 17 placed thereon.

[0084] The terminal box itself is therefore designed to be explosion pressure-resistant.

[0085] Between the lower part 15 and the cover 17 placed on it, a gap area that is as long and as thin as possible is formed in the contact area, so that a possible explosion wave loses so much energy when passing through the gap area that a propagation of the explosion through the gap area is prevented.

[0086] In addition, a seal, in particular a flat seal or O-ring, is arranged between the cover 17 and the lower part 15.

[0087] Between the lower part 15 and the first housing part 8, a gap area that is as long and as thin as possible is formed in the contact area, so that a possible explosion wave loses so much energy when passing through the gap area that a propagation of the explosion through the gap area is prevented.

[0088] In addition, a seal, in particular a flat seal or O-ring, is arranged between the cover 17 and the lower part 15. In particular, another such seal is arranged between the lower part 15 and the first housing part 8.

[0089] Radial regions of a plastic star are arranged in the circumferential direction between the claws of the shaft 2 and the claws of the coupling part 10, so that speed fluctuations can be dampened.

[0090] A gap as long and as thin as possible is formed in the contact area between the first housing part 8 and the second housing part 19 connected to it, so that any explosion wave loses so much energy upon passing through the gap that the explosion's propagation through the gap is prevented. For this purpose, the gap is at least four times as wide in the axial direction as in the radial direction, with the axial direction being parallel to the direction of the rotational axis of the shaft 2.

[0091] In addition, a seal, in particular a flat seal or O-ring, is arranged between the first housing part 8 and the second housing part 19 connected to it.

[0092] The flange part 1 is arranged outside the housing of the brake arrangement formed from the first housing part 8 and the second housing part 19 connected to it.

[0093] The second bearing 20 is preferably designed as a ball bearing, to which a cylindrical roller bearing or angular contact bearing is also assigned. The double bearing of the shaft 2 thus formed ensures that the alignment of the shaft 2 remains as unchanged as possible, especially when a significant transverse moment is introduced into the shaft 2 by the slip-on pinion. This is particularly important because there is a very narrow but axially long annular gap between the shaft 2 and the second housing part 19, preventing the explosion from spreading through the gap area. For this purpose, the annular gap is preferably at least fifty times wider in the axial direction than in the radial direction.

[0094] Likewise, such a narrow annular gap is also present between the shaft 2 and the first housing part 8, although the first bearing 9 of the shaft 2 is accommodated in the first housing part 8.

[0095] The first bearing 9 is arranged on the side of the first housing part 8 facing the magnetic body 3.

[0096] The double bearing, and thus the second bearing 20, is arranged on the side of the second housing part 19 facing the magnet body 3. In this way, after the brake is installed in the housing of the brake assembly, the housing is connected and cannot be opened by an insufficiently qualified person. However, such a person may very well connect the housing to the flange part 1 and the flange part 1 to the gearbox housing, and even replace the double bearing during maintenance beforehand, in particular without having to open the housing of the brake assembly.

[0097] Furthermore, a microswitch for monitoring brake pad wear is located on the brake assembly inside the housing of the brake assembly. The microswitch monitors the distance to the armature disk 5 when the coil 4 is in the de-energized state, i.e., when the current is off, to ensure it falls below a threshold value. This allows the microswitch to generate a warning signal when the brake pad wear has exceeded a critical level. However, a different distance sensor can also be used instead of the microswitch.

[0098] As in Figure 2As shown, manual brake release is possible. For this purpose, a bracket 21 is attached to a rotatably mounted rotating part 22, which has a non-circular, in particular eccentric, section 60. Thus, by pivoting the bracket 21, the rotating part 22 can be rotated, in particular about an axis of rotation oriented perpendicular to the axis of rotation of the shaft 2. As a result of the pivoting movement, the eccentric region 60, in particular section, is pressed onto the armature disk 5 in such a way that the armature disk 5 is pressed toward the magnet body 3, thereby releasing the brake.

[0099] As in Figure 5 As shown, the rotating part 22 is slide-mounted in a screw bushing 50. The screw bushing 50 is screwed into a threaded bore of the first housing part 8. The screw bushing 50 projects through the first housing part 8, in particular from the external environment to the interior area, which includes the brake.

[0100] At its outer end region, i.e., the end region facing the surroundings relative to the pivot axis of the rotating part 22, the screw bushing 50 has an external hexagon-like region. Thus, the screw bushing 50 can be screwed into the threaded bore of the first housing part 8 using a tool.

[0101] As in Figure 6 As shown, the rotating part 22 has a circumferential collar region 63, with which the rotating part rests on the end face of the screw bushing 50 facing the interior.

[0102] The rotating part 22 is preferably made of hardened steel. The screw bushing 50, on the other hand, is preferably made of a softer material, in particular copper or brass. The material of the screw bushing 50 is at least electrically conductive. The first housing part 8 is also made of steel. Thus, a plain bearing can be easily formed, and the heat dissipating in the event of an explosion is dissipated as it spreads between the rotating part 22 and the screw part, in particular the screw bushing, 50, in particular largely through the heat-conducting screw part, in particular the screw bushing, 50.

[0103] On the end face facing the external environment, the rotating part 22 has an axially projecting non-circular dome region 62 onto which the bracket 21 is placed with a non-circular recess extending through the bracket 21, so that the bracket 21 is connected to the rotating part 22 in a rotationally fixed manner.

[0104] The round section of the rotating part 22, which is arranged between the non-round section 60 and the dome section, in particular dome area, 62, is cylindrical and is received in the screw bushing 50, in particular is rotatably mounted in a sliding bearing.

[0105] Thus, a rotationally fixed connection of the bracket 21 with the rotating part 22 is provided, the rotating part 22 is received in the screw bushing 50 and mounted rotatably relative to it, wherein such a narrow gap is present between the screw bushing 50 and the rotating part 22, in particular the round area, in particular the section 61, that the arrangement is designed to be explosion pressure-resistant.

[0106] A return spring supported on the first housing part 8 is connected to the bracket 21, so that the bracket 21 returns to its original position after actuation, in particular after manually overcoming the spring force generated by the return spring. The return spring is preferably designed as a spiral spring or at least comprises a spiral spring. In particular, the return spring is made of a bent wire, the first end of which is bent and inserted into a recess in the bracket 21, and the second end of which is inserted into a recess in the first housing part 8.

[0107] As in Figure 3 As shown, the opening of the gearbox housing can also be covered without the flange part 1 by connecting the second housing part 19 to the gearbox housing, and the gearbox can be sealed oil-tight to the outside environment. Figure 3 the second housing part 19 has a correspondingly shaped, Figure 3 flange section facing the gearbox (not shown). In contrast to the embodiment according to Figure 2 The double bearing can also be replaced by a correspondingly large and stable single bearing, although this has the disadvantage that the wall thickness of the second housing part 19 must be reduced.

[0108] As in the Figures 7 to 10 As shown, the cable bushing 14 has a sealing element 70 with continuous recesses. Cables for supplying the electrical components of the brake assembly can be passed through these recesses, so that the connections can be provided in the terminal box. The cables are routed to the connection device 16, which is arranged in the lower part 15 and the cover 17 placed thereon. The cable bushing is designed to be explosion-proof in the following manner.

[0109] Recesses through the sealing element 70, through which no cable is passed, are filled with a pin 74 or 80. For this purpose, the pin 74 or 80 with the appropriate diameter is inserted into the respective recess.

[0110] Each of the recesses preferably has a constriction 73 in its center, so that the pin 74 or 80 must be pressed in with a force fit and thus a high degree of tightness can be achieved.

[0111] The first of the recesses associated with the pin 74 has a larger clear inner diameter than the second of the recesses associated with the pin 80.

[0112] The recesses of the sealing element 70 have different inner diameters. This allows for the passage of cables of different thicknesses.

[0113] The cable feedthrough 14 is arranged in a recess of the first housing part 8.

[0114] Here, the sealing element is inserted into a cylindrical bore, in particular one designed as a stepped bore, wherein the sealing element 70 preferably has a convex shape, in particular a barrel shape. The convex, in particular barrel-shaped, surface region 72 thus rests against the cylindrical bore, so that it is elastically deformed and thus a high degree of sealing is achieved.

[0115] The nut 71 is screwed with its external thread into a threaded bore of the first housing part 8, wherein the threaded bore is aligned coaxially to the cylindrical bore.

[0116] The end face of the sealing element 70 facing away from the nut 71 rests against a step in the cylindrical bore. Thus, the sealing element 70 is squeezed toward the cable passing through it and thus lies tightly against the wall of the cylindrical bore. The barrel-shaped outer circumference of the sealing element 70 also contributes to this.

[0117] The largest outer diameter of the convex, particularly barrel-shaped, surface area 72 is larger than the clear inner diameter of the cylindrical bore. Thus, the sealing element 70 is elastically stretched upon insertion into the cylindrical bore. Thus, the seal is already established upon insertion, but is further enhanced upon elastic deformation by screwing in the nut 71.

[0118] Since the recesses passing through the sealing element 70 have constrictions 73 and the pins (74, 80) are inserted into the unoccupied recesses passing through the sealing element 70 and thus elastically deform the constrictions 73, a further improved tightness is achieved.

[0119] Each of the pins has a conical insertion bevel at its first end and a widened head at its other end, with which the respective pin 74 or 80 rests against the sealing element 70, in particular against the end face of the sealing element 70 facing the screw bushing 71.

[0120] In further embodiments according to the invention, the first bearing 9 is also designed as a double bearing. List of reference symbols

[0121] 1 Flange part 2 Shaft 3 Magnet body 4 Coil 5 Armature disk 6 Brake pad carrier 7 Friction disk 8 First housing part 9 First bearing 10 Coupling part 11 Carrier disk 12 First circuit board 13 Permanent magnet 14 Cable gland, in particular explosion-proof 15 Lower part 16 Connection device 17 Cover 19 Second housing part 20 Second bearing 21 Bracket 22 Rotating part with non-circular, in particular eccentric, section 23 Driver 30 Spring element 40 Bearing holder 41 Support ribs 50 Screw bushing 60 Non-circular section of the rotating part 22 61 Round section of the rotating part 22 62 Dome section, in particular dome area 63 Collar area 70 Sealing element 71 Nut 72 Convex, in particular barrel-shaped, surface area 73 Constriction 74 First pin 80 Second pin

Claims

1. A drive, having: a gear unit with a gear unit housing; an electromagnetically actuated braking arrangement; and an electric motor, wherein the braking arrangement is arranged between the gear unit and the electric motor, wherein in a first housing part (8) of the braking arrangement there is received a first bearing (9) and in a second housing part (19) of the braking arrangement a second bearing (20), wherein a shaft (2) is rotatably mounted by means of the first and second bearings (20), wherein the shaft (2) is connected non-rotatably to a gearing part of the gear unit, in particular to a gearing part, in particular slip-on pinion, of the first gear stage of the gear unit, or is embodied in one piece, in particular therefore in one part, with this gearing part, wherein the shaft (2) protrudes through a magnet body (3), in particular through a ferromagnetic coil body, of the braking arrangement, wherein the shaft (2) is connected non-rotatably to a brake lining carrier (6) which is arranged in the axial direction between the first and the second bearing (20), wherein the brake lining carrier (6) is arranged so as to be displaceable relative to the shaft (2), in particular parallel to the axis of rotation of the shaft (2), characterised in that in the first housing part (8) there is arranged a cable bushing (14) which has a screw nut and a sealing element (70), with the sealing element (70) being inserted into a stepped bore and the screw nut being screwed into a threaded bore in the first housing part (8), with the threaded bore being oriented coaxially with the stepped bore, with the screw nut being positioned on the sealing element (70), in particular with the sealing element (70) being manufactured from rubber or from plastics material, with the sealing element (70) having continuous cutouts through each of which either a cable is guided or a pin (74) protrudes, with the cutouts being oriented in each case parallel to the bore axis of the cylindrical bore, with one of the cutouts having a larger clear internal diameter than another one of the cutouts.

2. A drive according to claim 1, characterised in that each of the cutouts has in each case at least one constriction (73) which is deformed by the respective cable or by the respective pin (74).

3. A drive according to claim 1 or 2, characterised in that the sealing element (70) is barrel-shaped and / or has at least one convex, in particular barrel-shaped, surface region (72).

4. A drive according to one of the preceding claims, characterised in that the sealing element (70) is adjusted against a step of the stepped bore.

5. A drive according to one of the preceding claims, characterised in that to the outside of the first housing part (8) is connected a lower part (15) on which a cover (17) is placed, so that electrical connection devices (16) are arranged and encased in the terminal box thus formed from the lower part (15) and the cover (17), with electric lines being guided through the explosion-pressure resistant cable bushing (14), which is arranged in a continuous cutout in the first housing part (8), in particular with the maximum pressure of the explosion-pressure resistant cable bushing (14) being 3 bar or more.

6. A drive according to one of the preceding claims, characterised in that a rotary part is rotatably mounted relative to the first housing part (8), in particular about an axis of rotation which is oriented perpendicularly to the axis of rotation of the shaft (2), with a screw bush (50) being screwed by its external thread into a threaded bore which passes through the first housing part (8) and the rotary part being received and rotatably mounted in the screw bush (50), with the rotary part protruding out of the screw bush (50) on either side, with the rotary part having an eccentric region which is in an operative connection with an armature disc (5) of the braking arrangement, in particular for manually actuated release of the braking arrangement.

7. A drive according to one of the preceding claims, characterised in that the screw bush (50) is manufactured from a softer material than the rotary part, in particular with the rotary part being manufactured from a hardened steel and the screwing part, in particular the screw bush (50), from a copper-containing material, in particular from a copper alloy and / or from brass.

8. A drive according to one of the preceding claims, characterised in that the rotary part has a collar region (63), in particular a collar region (63) designed to run around uninterrupted in the circumferential direction relative to the axis of rotation of the rotary part, with the collar region (63) being positioned on the screwing part, in particular with the collar region (63) protruding from the rotary part in the radial direction relative to the axis of rotation of the rotary part, and / or with the collar region (63) being arranged axially between the non-round region, in particular portion, and the round, in particular cylindrical, region, in particular portion, of the rotary part.

9. A drive according to one of the preceding claims, characterised in that the rotary part has a non-round dome region which protrudes into a cutout in a bracket (21), in particular for non-rotatably connecting the bracket (21) to the rotary part, and / or in that a restoring spring supported on the first housing part (8) is connected to the bracket (21), in particular with the restoring spring having a spiral spring and / or being produced from a wire, the first end of which is bent over and / or inserted into a cutout in the bracket (21) and the second end of which into a first housing part (8).

10. A drive according to one of the preceding claims, characterised in that the first housing part (8) is connected to the second housing part (19), in particular with the region of the contact of the first housing part (8) with the second housing part (19) being extended further in the axial direction than in the radial direction, and / or in that the shaft (2) is connected non-rotatably to the rotor shaft of the electric motor, and / or in that the shaft (2) has on its axial end region which faces the rotor shaft claws which are spaced apart from each other in the circumferential direction, with a coupling part (10) being connected non-rotatably to the rotor shaft, in particular by means of a feather-key connection, with the coupling part (10) on its axial end region which faces the shaft (2) having claws which are spaced apart from each other in the circumferential direction, with the region covered in the axial direction by the claws of the coupling part (10) overlapping with the region covered in the axial direction by the claws of the shaft (2), in particular with the claws of the coupling part (10) covering a radial distance region relative to the axis of rotation of the shaft (2) which is also covered by the claws of the shaft (2).

11. A drive according to one of the preceding claims, characterised in that the brake lining carrier (6) is arranged axially movably relative to the shaft (2), in particular with there being mounted on the shaft (2) a driving element (23) which in the circumferential direction is connected in a form-fit to the shaft (2) and / or which is connected in a form-fit to the shaft (2) by means of a feather-key connection, with the driving element (23) having external gearing which meshes with the internal gearing of the brake lining carrier, and / or in that an armature disc (5) of the braking arrangement is connected non-rotatably and is connected axially movably to the magnet body (3), with spring elements (30) supported on the magnet body (3) pressing on the armature disc (5), in particular applying spring force to the armature disc (5), with the armature disc (5) being arranged between, in particular axially between, the magnet body (3) and the brake lining carrier (6), in particular with the magnet body (3) and / or the armature disc (5) being manufactured from ferromagnetic material.

12. A drive according to one of the preceding claims, characterised in that a friction disc (7) of the braking arrangement is connected to the magnet body (3), in particular by means of bolts which protrude into the magnet body (3) and guide the armature disc (5), in particular with the friction disc (7) being connected to the first housing part (8).

13. A drive according to one of the preceding claims, characterised in that the brake, comprising the magnet body (3), the coil (4), the spring elements (30), the armature disc (5), the brake lining carrier (6), the friction disc (7) and bolts, is formed preassembled and / or in that the magnet body (3), the coil (4), the spring elements (30), the armature disc (5), the brake lining carrier (6), the friction disc (7) and bolts are surrounded and / or encased by the housing formed from the first and second housing part (8).

14. A drive according to one of the preceding claims, characterised in that in a first rotary position of the rotary part the eccentric region presses the armature disc (5), counter to the spring force generated by the spring elements (30), towards the magnet body (3), and in a second rotary position of the rotary part the armature disc (5) is movable in the axial direction, i.e. in the direction of the axis of rotation of the shaft (2), such that the armature disc (5) presses the brake lining carrier (6) onto the friction disc (7), in particular when the coil (4) is non-energised, in particular with the rotary part being connected to a holding bracket, in particular with the holding bracket extending at least in portions, in particular relative to the axis of rotation of the shaft (2), tangentially and / or in the circumferential direction.

15. A drive according to one of the preceding claims, characterised in that to the second housing part (19) there is connected a flange part (1) which covers an opening in the gear unit housing and / or closes it in particular in an oil-tight manner, and / or in that a first printed circuit board (12) is connected non-rotatably to the first housing part (8), with a second, in particular therefore further, printed circuit board being connected non-rotatably to the shaft (2), with the first printed circuit board (12) being equipped with electronic components such that the angular position of the second printed circuit board and / or of the shaft (2) is detectable, in particular with the first printed circuit board (12) being arranged parallel to the second printed circuit board, and / or with the first printed circuit board (12) being pressed against the first housing part (8) by the friction disc (7), in particular with the second printed circuit board being arranged axially between the first printed circuit board (12) and the first housing part (8), and / or in that a sensor for detecting the brake lining wear is arranged in the housing formed from the first and second housing parts (8), in particular with the sensor lines being guided through the cable bushing (14), and / or in that an annular gap is arranged between the first housing part (8) and the shaft (2), in particular the axial length of which is greater than the radius of the annular gap, with the annular gap being arranged on that side of the first bearing (9) which faces away from the magnet body (3) and / or from the second bearing (20), in particular being arranged on that side of the first bearing (9) which faces away from the magnet body (3) and / or from the second bearing (20) in the axial direction, and / or in that the second bearing (20) is embodied as a duplex bearing, in particular with the second bearing (20) having at least one cylindrical roller bearing, and / or in that a further annular gap is arranged between the second housing part (19) and the shaft (2), in particular the axial length of which is greater than the radius of the further annular gap, with the second bearing (20) being arranged on that side of the further annular gap which faces away from the magnet body (3) and / or from the first bearing (9), in particular being arranged on that side of the further annular gap which faces away from the magnet body (3) and / or from the first bearing (9) in the axial direction.