drive comprising a gearbox with a gearbox housing, an electromagnetically actuated brake arrangement and an electric motor

Abstract

Drive comprising a gearbox with a gearbox housing, an electromagnetically actuated brake arrangement and an electric motor, the brake assembly is located between the gearbox and the electric motor, wherein a first bearing is accommodated in a first housing part (8) of the brake assembly and a second bearing (20) is accommodated in a second housing part (19) of the brake assembly, wherein a shaft (2) is rotatably mounted by means of the first and second bearings (20), wherein the shaft (2) is non-rotatably connected to a toothed part of the transmission or is integrally formed with this toothed part, wherein the shaft (2) protrudes through a magnetic body (3) of the brake arrangement, wherein the shaft (2) is non-rotatably connected to a brake pad carrier (6) which is arranged in the axial direction between the first and the second bearing (20), characterized by the fact that in the first housing part (8) a cable gland (14) is arranged, which has a screw nut and a sealing element (70), wherein the sealing element (70) is inserted into a stepped bore and the screw nut is screwed into a threaded bore of the first housing part (8), wherein the threaded bore is aligned coaxially with the stepped bore, where the screw nut rests against the sealing element (70), wherein the sealing element (70) has continuous recesses through which either a cable is passed or a pin (74) protrudes.

Description

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

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

[0003] From DE 20 2010 000 709 U1, an electromechanical actuator is known as the closest prior art.

[0004] Cable glands are known from page 74 of an order catalog of the company Plitsch.

[0005] A gearbox is known from EP 2 677 197 A1.

[0006] An electromagnetically actuated brake is known from DE 10 2014 018 485 B3.

[0007] An electromagnetically actuated brake arrangement is known from US 2021 / 0 131 512 A1.

[0008] From DE 79 28 392 U1 a hermetically sealed entry for a cable harness is known.

[0009] An electric motor is known from DE 10 2010 049 748 A1.

[0010] From DE 10 2010 049 747 A1 a kit for the production of different electric motors is known.

[0011] A brake is known from DE 10 2010 049 744 A1.

[0012] An adapter for a drive is known from DE 10 2019 003 545 A1.

[0013] A drive with adapter is known from DE 10 2019 003 546 A1.

[0014] The invention is therefore based on the objective of achieving increased safety in a drive system.

[0015] According to the invention, the problem is solved in the drive according to the features specified in claim 1.

[0016] Key features of the drive include a gearbox with a gearbox housing, an electromagnetically actuated brake assembly, and an electric motor, with the brake assembly being located 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 non-rotatably connected to a toothed part of the transmission, in particular to a toothed part, in particular a pinion, of the first gear stage of the transmission, or is integrally formed, in particular in one piece, with this toothed part, wherein the shaft protrudes through a magnetic body, in particular through a ferromagnetic coil body, of the braking arrangement, 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 cable gland 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 with the stepped bore, where the screw nut rests against the sealing element, especially where the sealing element is made of rubber or plastic, in particular wherein the brake pad carrier is arranged to be displaceable relative to the shaft, especially parallel to the axis of rotation of the shaft.

[0017] An advantage of this design is the increased safety it provides. This is achieved through a sealing element that sits in a stepped bore and is held in place by a screw nut. This elastic deformation of the sealing element ensures that its outer circumference fits snugly against the wall of the stepped bore and also against the cables and pins passing through it. This creates an explosion-proof cable penetration. The cables from the coil and the sensor(s) of the brake assembly can be routed through the wall of the second housing part into the interior of a junction box, which is hermetically sealed off from the interior of the brake assembly containing the brake itself. In particular, manual release of the brake is also possible from the outside through the second housing part by means of a rotating component. This ensures safe operation even in potentially explosive atmospheres.

[0018] The term "explosion-proof" here means that the cable gland can withstand an overpressure, particularly in the event of an explosion, of at least 3 bar. The maximum pressure for the cable gland is therefore preferably 3 bar.

[0019] In an advantageous embodiment, the sealing element has continuous recesses through which either a cable is passed or a pin protrudes, in particular wherein the recesses are each aligned parallel to the bore axis of the cylindrical bore, In particular, one of the recesses has a larger clear inner diameter than another of the recesses. An advantage of this is that none of the recesses are unfilled. Thus, a high degree of tightness is achieved.

[0020] In an advantageous embodiment, each of the recesses has at least one constriction, which is deformed by the respective cable or pin. An advantage of this is that improved sealing can be achieved, since the pin is connected by friction.

[0021] In an advantageous embodiment, the sealing element is barrel-shaped and / or has at least one convex, particularly barrel-shaped, surface area. An advantage of this is that elastic deformation can be achieved as soon as it is inserted into the recess. Thus, a seal is established immediately upon insertion.

[0022] In an advantageous embodiment, the sealing element is positioned against a step of the stepped bore. It is advantageous that the diameter of the sealing element is larger than the clear inner diameter at the step of the stepped bore. Thus, the screw bushing presses the sealing element against the step and deforms it in such a way that a high degree of sealing against the first housing is achieved, meaning that the cables and pins are sealed against the first housing part.

[0023] In an advantageous embodiment, 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 non-rotatably connected to a toothed part of the transmission, in particular to a toothed part, in particular a pinion, of the first gear stage of the transmission, or is integrally formed, in particular in one piece, with this toothed part, wherein the shaft protrudes through a magnetic body, in particular through a ferromagnetic coil body, of the braking arrangement, 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 an axis of rotation which is oriented perpendicular to the axis of rotation of the shaft, wherein a screw bushing with its external thread is screwed 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 area which is in operative connection with an anchor disk of the brake assembly, in particular for manually actuated release of the brake assembly, in particular wherein the brake pad carrier is arranged to be displaceable relative to the shaft, especially parallel to the axis of rotation of the shaft.

[0024] An advantage of this design is that the rotating part is received in the screw bushing in such a way that a cylindrical section is accommodated in an inner cylindrical recess of the screw bushing and rests against it in such a manner that the brake assembly is explosion-proof, and in particular, that an explosion front cannot propagate between the screw bushing and the rotating part. This allows for manual rotation of the rotating part by pivoting the bracket, thereby rotating the part within the screw bushing. This causes the non-circular section, in particular the area, of the rotating part to lift the armature disc of the brake assembly against the spring force acting on the armature disc of the brake assembly, i.e., to push it away from the brake pad carrier.

[0025] In an advantageous embodiment, the screw bushing is made of a softer material than the turned part. in particular wherein the turned part is made of hardened steel and the screwed part is made of a copper-containing material, in particular a copper alloy and / or of

[0026] Brass. An advantage here is that the turned part is mounted in a plain bearing and therefore has minimal bearing clearance. Furthermore, copper is a very good thermal conductor, so that an explosion front attempting to propagate between the screw bushing and the turned part dissipates heat very quickly, and its propagation can thus be prevented even more rapidly than with less thermally conductive materials.

[0027] In an advantageous embodiment, the turned part has a collar area, in particular a collar area that extends continuously around the circumference in relation to the axis of rotation of the turned part. where the collar area rests against the screw part, In particular, wherein the collar area projects radially from the turned part with respect to the axis of rotation of the turned part, and / or wherein the collar area is arranged axially between the non-circular area and the round, in particular cylindrical, section, in particular area, of the turned part. An advantage of this is that axial limitation and / or positioning is easily enabled.

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

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

[0030] In an advantageous embodiment, 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 non-rotatably connected to a toothed part of the transmission, in particular to a toothed part, in particular a pinion, of the first gear stage of the transmission, or is integrally formed, in particular in one piece, with this toothed part, wherein the shaft protrudes through a magnetic body, in particular through a ferromagnetic coil body, of the braking arrangement, 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, in particular wherein the brake pad carrier is arranged to be displaceable relative to the shaft, especially parallel to the axis of rotation of the shaft.

[0031] An advantage of this design is the low operating costs, as maintenance can be performed even by non-specially qualified personnel. In particular, the brake assembly is explosion-proof and therefore may only be opened by specially qualified personnel. However, the entire brake assembly can be removed from the drive unit by non-specially qualified personnel and replaced with a different brake assembly.

[0032] This allows for cost-effective maintenance. Furthermore, this personnel is also authorized to service the electric motor and gearbox, including opening the gearbox, topping up the oil, or replacing a gear component.

[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 thereby reducing operating costs, particularly through timely maintenance and damage prevention.

[0034] It is also important that the brake pad carrier is slidably mounted, so that the braking effect is essentially independent of the wear condition of the brake pads on the carrier. Minor wear can be compensated for by this movement. This also increases operational safety.

[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 extended further in the axial direction than in the radial direction. An advantage of this is that the brake can be provided in an explosion-proof housing. Thus, the brake is encapsulated and can be arranged as a transportable unit between the motor and the gearbox.

[0036] In an advantageous embodiment, the shaft is rotationally fixed to the rotor shaft of the electric motor. A further advantage is that the shaft can be connected to the rotor shaft via a coupling, in particular a jaw coupling. This allows a coupling function to be integrated into the braking arrangement. The braking arrangement thus also acts as an adapter between the motor and gearbox, compensating for deviations of the rotor shaft's axis of rotation from the shaft's axis of rotation.

[0037] In an advantageous embodiment, the shaft has claws spaced apart from each other 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 each other in the circumferential direction at its axial end region facing the shaft, wherein the area covered in the axial direction by the claws of the coupling part overlaps with the area covered in the axial direction by the claws of the shaft, In particular, the claws of the coupling component cover a radial spacing range relative to the shaft's axis of rotation, which is also covered by the shaft's claws. An advantage of this is that the coupling, and especially the coupling component, allows for tolerance compensation. Therefore, if the rotor shaft's axis of rotation and the shaft are not perfectly aligned, the coupling, and especially the coupling component, transmits torque and dampens lateral torques. Furthermore, plastic material, particularly a star-shaped plastic star, can be provided between the claws to dampen speed fluctuations.

[0038] In an advantageous embodiment, the brake pad carrier is arranged to be axially movable relative to the shaft, in particular wherein a driver is mounted on 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 connection, wherein the driver has external teeth which engage with the internal teeth of the brake pad carrier. It is advantageous that the brake pad carrier initially compensates for the wear of the brake pads through its movement. With thinner brake pads and a de-energized coil, the spring elements, via the armature disc, press the brake pad carrier closer to the friction disc. Thus, operational reliability is high. Furthermore, the wear is monitored for exceeding a permissible limit by a sensor arranged on the brake, in particular a microswitch or inductive proximity sensor.This also further increases operational reliability.

[0039] In an advantageous embodiment, an armature disk is connected to the magnet body in a rotationally fixed manner and is axially movable. wherein spring elements supported on the magnet body press against the armature disk, in particular acting on the armature disk with spring force, wherein the armature disk is arranged between, in particular axially between, the magnet body and the brake pad carrier, In particular, the magnet body and / or the armature disc are made of ferromagnetic material. An advantage of this is the increased operational reliability, as the brake engages automatically 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 which project into the magnetic body and guide the armature disc. In particular, the friction disc is connected to the first housing part. An advantage of this design is that the brake is pre-assembled, trainable, and thus safety is increased.

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

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

[0043] In an advantageous embodiment, a rotating part is rotatably mounted relative to the first housing part, in particular about an axis of rotation that is aligned perpendicular to the axis of rotation of the shaft. the turned part has an eccentric area, wherein in a first rotational position of the rotating part the eccentric area presses the armature disk towards the magnet 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 such a way in the axial direction, i.e. in the direction of the axis of rotation of the shaft, that the armature disk presses the brake pad carrier onto the friction disc, especially when the coil is unenergized, In particular, wherein the rotating part is connected to a retaining bracket, and in particular wherein the retaining bracket extends at least sectionally, in particular with respect to the axis of rotation of the shaft, tangentially and / or circumferentially. It is advantageous that manual release, i.e., manually activated release of the brake, is achievable. For this purpose, a retaining bracket is pivoted, thereby rotating the rotating part such that the eccentric part of the rotating part pushes 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 is connected to the second housing part, which covers an opening in the gearbox housing and / or, in particular, seals it oil-tight. The advantage here is that the brake assembly, with its entire housing, can be connected to the gearbox via the flange and is secured to the gearbox. In particular, the motor can be attached to the housing of the brake assembly and secured by this housing. Furthermore, this allows even non-specially qualified personnel to connect the brake assembly to the gearbox and then fill the gearbox with oil. The brake, which is encapsulated in the housing of the brake assembly, does not need to be opened. The flange covers the gearbox opening, allowing the gearbox to be filled with oil afterward. In a further development, the second housing part of the brake assembly can even be used directly to cover the gearbox opening. A flange 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 enclosed in the connection box formed from the lower part and the cover. Electrical cables are routed through an explosion-proof cable gland located in a continuous recess in the first housing section. A key advantage is that the junction box itself is explosion-proof. This allows for the electrical connections to be planned for and located within the explosion-proof area. Furthermore, this section of the junction box is separated from the brake area and connected only via a cable gland. Therefore, an explosion cannot propagate from the brake area to the connection area, and vice versa. This significantly increases safety.

[0046] In an advantageous embodiment, a first circuit board is connected to the first housing part in a rotationally fixed manner. wherein a second, in particular another, circuit board is non-rotatably connected to the shaft, 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 wave can be detected, 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, and in particular wherein the second printed circuit board is arranged axially between the first printed circuit board and the first housing part. It is advantageous that the first printed circuit board can be arranged in a clamping manner and is therefore cost-effective to connect.

[0047] In an advantageous embodiment, a sensor for detecting brake pad wear is arranged in the housing formed from the first and second housing parts. In particular, the sensor cables are routed through the cable gland. An advantage of this is that 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 magnet body and / or the second bearing, in particular on the side of the first bearing facing away from the magnet body and / or the second bearing in the axial direction. It is advantageous that the annular gap is designed to be so narrow and axially long that penetration by an explosion front is prevented. Furthermore, the first bearing can be arranged in the explosion-pressure-resistant area, thus increasing operational safety because the rotation 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. The advantage here is that 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 even under fluctuating transverse forces, and in particular does not change measurably.

[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, The second bearing is arranged on the side of the annular gap facing away from the magnet body and / or the first bearing, in particular on the side of the annular gap facing away from the magnet body and / or the first bearing in the axial direction. An advantage of this is that the second bearing is accessible and replaceable from the outside without having to open the housing of the brake assembly. Thus, no special qualifications of a specialist are required. The thickness of the annular gap does not change, even under fluctuating lateral forces, and in particular, this change is not measurable.

[0051] Further advantages arise from the dependent claims. The invention is not limited to the combination of features of the claims. For those skilled in the art, further meaningful combinations of claims and / or individual claim features and / or features of the description and / or the figures will become apparent, in particular from the problem statement and / or the problem arising from a comparison with the prior art.

[0052] The invention will now be explained in more detail with reference to schematic illustrations: In the Fig. Figure 1 shows a cross-section through a brake arrangement according to the invention. In the Fig. Figure 2 shows an oblique view of a sectioned representation of the brake assembly. In the Fig. Figure 3 shows a cross-section of another brake arrangement. In the Fig. Figure 4 shows an oblique view of the brake assembly. In the Fig. Figure 5 shows an enlarged cross-section of an area of ​​the brake assembly, which shows a rotating part 22. In the Fig. Figure 6 shows the turned part 22 in oblique view. In the Fig. Figure 7 shows the cable entry 14 in cross-section. In the Fig. Figure 8 shows pins (74, 80) of the cable entry 14 in oblique view. In the Fig. Figure 9 shows a seal 70 of the cable gland 14 in oblique view. In the Fig. Figure 10 shows a nut 71 of the cable gland 14 in oblique view.

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

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

[0055] For example, the coupling part 10 is designed in a sleeve-like form and is placed on the rotor shaft, which is not shown in the figures, and connected in a rotationally fixed manner, in particular by means of a keyway 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, allowing a pinion gear to be mounted onto shaft 2 and connected to the shaft in a rotationally fixed manner by means of a key. The pinion gear has external teeth and functions as the driving gear element of the first gear stage of the transmission.

[0058] Shaft 2 has claws at its axial end facing away from the gearbox and / or gearing section. These claws are operatively connected to claws formed on the coupling part 10, forming a claw coupling. For this purpose, the claws of shaft 2 are spaced apart from each other in the circumferential direction, in particular regularly, and project into the spaces created by the circumferential spacing of the claws of the coupling part 10. In this way, shaft 2 is positively connected to the coupling part 10 in the circumferential direction.

[0059] The shaft 2 is rotatably mounted by means of a first bearing 9 received in a first housing part 8 and by means of a bearing 20 received 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 by means of screws.

[0061] When the flange part 1 is connected to the gearbox housing, an opening in the gearbox 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 gearbox via the brake assembly.

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

[0063] A shaft seal ring included in the second housing part 19 seals against the 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 connection. On its radially outer circumference, the driver has external teeth onto which a brake pad carrier 6 is pushed, wherein an internal toothing of the brake pad carrier 6 engages with the external toothing. In particular, the brake pad carrier 6 is thus rotationally fixed to the driver 23 and axially displaceable relative to the driver 23.

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

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

[0067] The armature disk 5 is preferably made of ferromagnetic material. While the armature disk 5 is rotationally fixed to the magnet body 3, it is arranged to be movable in the axial direction, i.e., in the direction of the axis of rotation of the shaft 2. For this purpose, bolts are preferably inserted or screwed into axially oriented bores in the magnet body 3, which pass 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 against the armature disk 5, so that the armature disk 5 is pressed towards the brake pad carrier 6 by the spring force generated by the spring elements 30 when the coil 4 is de-energized. In this process, the brake pad carrier 6 is pressed by the armature disk 5 towards a braking surface formed on a friction disk 7. The friction disk 7 is connected to the first housing part 8, in particular rigidly connected.

[0070] However, when the coil 4 is energized, the armature disk 5 is pulled towards the magnet body 3 against the spring force generated by the spring elements 30, thus releasing the brake.

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

[0072] This design makes it possible to pre-assemble the elements related to the braking function and then install them in the housing of the brake assembly.

[0073] The pre-completed training is made from - the magnetic body 3 together with spring elements and the coil 4 contained therein, - the anchor disc, - the bolts that guide the anchor disc and The stack formed by the brake pad carrier is assembled as a pre-completed 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 magnetic body 3 via bolts, the bolts being inserted into bores in the magnetic body. The friction disc 7 is, for example, screwed to the bolts. The bolts are preferably axially aligned.

[0074] When installing the brake into the housing of the brake assembly, the friction disc 7 is connected to the first housing part 8 by means of screws, the screws being 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 circumferential, ring-shaped 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 fixed to shaft 2. Thus, the second circuit board is arranged to be rotatable relative to the first circuit board 12.

[0079] In conjunction with the permanent magnets, a sensor is implemented using the circuit boards, so that the angular position of shaft 2 can be detected by the sensor.

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

[0081] However, other operating principles are also foreseeable that do not require permanent magnets.

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

[0083] The sensor signals from the first circuit board 12 are routed via a cable through an explosion-proof cable gland 14 into a junction box located on the outside of the first housing part 8. This junction box is formed by placing a ring-shaped base 15 and a cover 17 on top of it.

[0084] The junction box itself is therefore designed to be explosion-proof.

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

[0086] Furthermore, 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 any explosion wave passing through the gap area loses so much energy that a propagation of the explosion through the gap area is prevented.

[0088] Furthermore, 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] In the circumferential direction between the claws of shaft 2 and the claws of the coupling part 10, radial areas of a plastic star are arranged so that speed fluctuations can be dampened.

[0090] Between the first housing part 8 and the second housing part 19 connected to it, a gap of the longest possible length and the thinnest possible width is formed in the contact area, so that any explosion wave passing through the gap loses so much energy that its propagation through the gap is prevented. For this purpose, the gap is at least four times wider in the axial direction than in the radial direction, with the axial direction being parallel to the direction of rotation of the shaft 2.

[0091] Furthermore, 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 assembly 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 thus formed for the shaft 2 ensures that the shaft 2 remains as straight as possible, especially when a significant transverse moment is introduced into the shaft 2 by the pinion gear. 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, thus preventing the explosion from propagating through the gap. 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, whereby 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 magnet body 3.

[0096] The double bearing, and thus the second bearing 20, is located 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 indeed connect the housing to the flange part 1 and connect the flange part 1 to the gearbox housing, and during maintenance, even replace the double bearing beforehand, particularly without having to open the housing of the brake assembly.

[0097] Furthermore, a microswitch for monitoring brake pad wear is located within the brake assembly housing. This microswitch monitors the distance to the armature disk 5 when the coil 4 is in its de-energized state (i.e., without current), checking for a threshold value. Thus, a warning signal can be generated by the microswitch when the brake pad has exceeded a critical wear level. However, an alternative distance sensor can also be used instead of the microswitch.

[0098] As in Fig. As shown in Figure 2, manual release of the brake 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 which is oriented perpendicular to the axis of rotation of the shaft 2. As a result of the pivoting movement, the eccentric section 60 is pressed against the armature disk 5 such that the armature disk 5 is pushed towards the magnet body 3 and the brake is thereby released.

[0099] As in Fig. As shown in Figure 5, the rotating part 22 is mounted in a threaded bushing 50. The threaded bushing 50 is screwed into a threaded bore of the first housing part 8. The threaded bushing 50 projects through the first housing part 8, specifically from the outer surroundings to the inner area, which includes the brake.

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

[0101] As in Fig. As shown in Figure 6, the turned part 22 has a circumferential collar area 63 with which the turned part abuts the end face of the screw bushing 50 facing the interior.

[0102] The turned 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 sliding bearing can be easily designed, and the heat propagating in the event of an explosion is dissipated as it spreads between the turned part 22 and the screw part, in particular the screw bushing 50, especially largely through the heat-conducting screw part, in particular the screw bushing 50.

[0103] On the end face facing the external environment, the turned part 22 has an axially projecting non-circular dome area 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 turned 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 rotatably by 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 rotatably mounted to it, wherein such a narrow gap is present between screw bushing 50 and rotating part 22, in particular round area, in particular 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 initial position after actuation, in particular after manually overcoming the spring force generated by the return spring. The return spring is preferably designed as a coil spring or at least has a coil spring. In particular, the return spring is made of a bent wire, the first end of which is bent over 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 Fig. As shown in Figure 3, even without flange part 1, the opening of the gearbox housing can be covered by connecting the second housing part 19 to the gearbox housing, thus sealing the gearbox oil-tight to the outside environment. For this purpose, see Figure 3. Fig. 3 the second housing part 19 a correspondingly shaped one, which is in the Fig. 3. Flange section facing the gearbox (not shown). In contrast to the embodiment shown below. Fig. 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 Fig. As shown in Figures 7 to 10, the cable gland 14 has a sealing element 70 with through-holes. Cables supplying the electrical components of the brake assembly can be routed through these holes, allowing connections to be made in the terminal box. The cables are routed to the connection device 16, which is located in the lower part 15 and the cover 17 placed thereon. The cable gland is designed to be explosion-proof.

[0109] Through-holes in the sealing element 70, through which no cable passes, are filled by a pin 74 or 80. For this purpose, the pin 74 or 80, which matches the 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 forcefully and thus a high degree of tightness can be achieved.

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

[0112] The recesses of the sealing element 70 have different clear inner diameters. This allows cables of varying thicknesses to pass through.

[0113] The cable gland 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 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 area 72 thus rests against the cylindrical bore, so that it is elastically deformed and therefore a high degree of sealing is achieved.

[0115] The nut 71 is screwed into a threaded bore of the first housing part 8 with its external thread, the threaded bore being 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. This compresses the sealing element 70 in the direction of the cables passing through it, ensuring it fits snugly against the wall of the cylindrical bore. The barrel-shaped outer circumference of the sealing element 70 also contributes to this effect.

[0117] The largest outer diameter of the convex, in particular barrel-shaped, surface area 72 is larger than the clear inner diameter of the cylindrical bore. Thus, the sealing element 70 is elastically stretched as soon as it is inserted into the cylindrical bore. The seal is therefore already formed upon insertion, but is further improved by elastic deformation when the nut 71 is screwed in.

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

[0119] Jeder der Stifte weise an seinem ersten Ende eine konische Einführschräge auf und an seinem anderen Ende einen verbreiterten Kopf, mit dem der jeweilige Stift 74 oder 80 am Dichtelement 70 anliegt, insbesondere an der der Schraubbuchse 71 zugewandten Stirnseite des Dichtelements 70.

[0120] In further embodiments according to the invention, the first bearing 9 is also designed as a double bearing. Reference symbol list 1 flange part 2nd wave 3 magnetic bodies 4 coils 5 Anchor disc 6 brake pad carriers 7 friction disc 8 first housing part 9 first camp 10 Coupling part 11 Carrier disc 12 first circuit board 13 Permanent magnet 14 Cable feedthrough, especially explosion pressure resistant 15 Lower part 16 Connection device 17 lids 19 second housing part 20 second camp 21 irons 22 Turned part with non-circular, in particular eccentric, section 23 drivers 30 spring element 40 Bearing intake 41 supporting ribs 50 screw bushing 60 non-circular section of the turned part 22 61 round section of the turned part 22 62 Cathedral section, especially cathedral area 63 Collar area 70 Sealing element 71 mother 72 convex, especially barrel-shaped, surface area 73 Narrowing 74 first pen 80 second pen

Claims

[1] Drive comprising a gearbox with a gearbox housing, an electromagnetically actuated brake assembly and an electric motor, the brake assembly is located between the gearbox and the electric motor, wherein a first bearing is accommodated in a first housing part (8) of the brake assembly and a second bearing (20) is accommodated in a second housing part (19) of the brake assembly, wherein a shaft (2) is rotatably mounted by means of the first and second bearings (20), wherein the shaft (2) is non-rotatably connected to a toothed part of the transmission or is integrally formed with this toothed part, wherein the shaft (2) protrudes through a magnetic body (3) of the brake arrangement, wherein the shaft (2) is non-rotatably connected to a brake pad carrier (6) which is arranged in the axial direction between the first and the second bearing (20), characterized by , that in the first housing part (8) a cable gland (14) is arranged, which has a screw nut and a sealing element (70), wherein the sealing element (70) is inserted into a stepped bore and the screw nut is screwed into a threaded bore of the first housing part (8), wherein the threaded bore is aligned coaxially with the stepped bore, where the screw nut rests against the sealing element (70), wherein the sealing element (70) has continuous recesses through which either a cable is passed or a pin (74) protrudes. [2] Drive according to claim 1, characterized by that the recesses are each aligned parallel to the bore axis of the cylindrical bore. [3] Drive according to any of the preceding claims, characterized by , that each of the recesses has at least one constriction (73) which is deformed by the respective cable or by the respective pin (74), and / or that the sealing element (70) is barrel-shaped and / or has at least one convex surface area (72), and / or that the sealing element (70) is positioned against a step of the stepped bore. [4] Drive according to any of the preceding claims, characterized by , that a lower part (15) is connected to the outside of the first housing part (8), on which a cover (17) is placed, so that electrical connection devices (16) are arranged and enclosed in the terminal box formed from the lower part (15) and the cover (17), wherein electrical conductors are guided through the explosion-proof cable gland (14), which is arranged in a continuous recess of the first housing part (8), and / or that a rotating part (22) is rotatably mounted relative to the first housing part (8), which is aligned perpendicular to the axis of rotation of the shaft (2), wherein a screw bushing (50) is screwed with its external thread into a threaded bore through the first housing part (8) and the rotating part (22) is received in the screw bushing (50) and rotatably mounted, wherein the rotating part (22) protrudes from the screw bushing (50) on both sides, wherein the rotating part (22) has an eccentric area which is operatively connected to an anchor disk (5) of the brake arrangement, and / or that the screw bushing (50) is made of a softer material than the turned part (22), and / or that the turned part (22) has a collar area (63), where the collar area (63) abuts the screw part. [5] Drive according to claim 4, characterized by , that the rotating part (22) has a non-circular dome area which projects into a recess of a bracket (21), and / or that a return spring supported on the first housing part (8) is connected to the bracket (21). [6] Drive according to any of the preceding claims, characterized by , that the first housing part (8) is connected to the second housing part (19), and / or that the shaft (2) is connected to the rotor shaft of the electric motor in a rotationally fixed manner, and / or that the shaft (2) has claws spaced apart from each other in the circumferential direction at its axial end region facing the rotor shaft, wherein a coupling part (10) is connected to the rotor shaft in a rotationally fixed manner, wherein the coupling part (10) has claws spaced apart from each other in the circumferential direction at its axial end region facing the shaft (2), wherein the area covered in the axial direction by the claws of the coupling part (10) overlaps with the area covered in the axial direction by the claws of the shaft (2). [7] Drive according to one of the preceding claims, characterized by , that the brake pad carrier (6) is arranged to be axially movable relative to the shaft (2), wherein the driver (23) has an external toothing which engages with the internal toothing of the brake pad carrier (6), and / or that an armature disk (5) of the brake assembly is connected to the magnet body (3) in a rotationally fixed manner and is connected axially movable, wherein spring elements (30) supported on the magnet body (3) press on the armature disk (5), wherein the armature disk (5) is arranged between the magnet body (3) and the brake pad carrier (6). [8] Drive according to any of the preceding claims, characterized by , that a friction disc (7) of the brake assembly is connected to the magnetic body (3). [9] Drive according to one of the preceding claims, characterized by , that the brake, comprising the magnet body (3), the coil (4), the spring elements (30), the armature disc (5), the brake pad carrier (6), the friction disc (7) and bolts, is pre-assembled and / or that the magnet body (3), the coil (4), the spring elements (30), the armature disc (5), the brake pad carrier (6), the friction disc (7) and bolts are surrounded and / or enclosed by the housing formed from the first and second housing parts (8, 19). [10] Drive according to claim 4, characterized by , that in a first rotational position of the rotating part (22) the eccentric area pushes the armature disk (5) towards the magnet body (3) against the spring force generated by the spring elements (30) and in a second rotational position of the rotating part (22) the armature disk (5) is movable in such a way in the axial direction, i.e. in the direction of the axis of rotation of the shaft (2) that the armature disk (5) presses the brake pad carrier (6) onto the friction disk (7). [11] Drive according to any of the preceding claims, characterized by , that a flange part (1) is connected to the second housing part (19), which covers and / or closes an opening of the gearbox housing, and / or that a first circuit board (12) is connected to the first housing part (8) in a rotationally fixed manner, wherein a second circuit board is connected to the shaft (2) in a rotationally fixed manner, wherein the first circuit board (12) is equipped with electronic components in such a way that the angular position of the second circuit board and / or the shaft (2) is detectable, and / or that a sensor for detecting brake pad wear is arranged in the housing formed from the first and second housing parts (8, 19), and / or that an annular gap is arranged between the first housing part (8) and the shaft (2), wherein the annular gap is arranged on the side of the first bearing facing away from the magnetic body (3) and / or the second bearing (20), and / or that the second bearing (20) is designed as a double bearing, and / or that a further annular gap is arranged between the second housing part (19) and the shaft (2), wherein the second bearing (20) is arranged on the side of the further annular gap facing away from the magnetic body (3) and / or from the first bearing.

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