Gear motor, especially for chain conveyors

Abstract

Gear motor, especially for chain conveyors, wherein the geared motor comprises a gear driven by an electric motor, wherein an electromagnetically actuated brake is arranged at the end of the rotor shaft of the electric motor facing away from the gear unit axially, in particular in a direction parallel to the axis of rotation of the rotor shaft of the electric motor, wherein the brake is housed, in particular surrounded, by the housing of the electric motor.

Description

The invention relates to a geared motor, in particular for a chain conveyor.It is generally known that in a chain drive, a chain is driven by a motor.The invention is therefore based on the object of making the geared motor robust.According to the invention, the object is achieved in the geared motor according to the features specified in claim 1.Important features in the geared motor, in particular for a chain conveying device, are that the geared motor has a gear driven by an electric motor, wherein an electromagnetically actuatable brake is arranged on the end of the rotor shaft of the electric motor facing away from the gear axially, in particular in a direction parallel to the axis of rotation of the rotor shaft of the electric motor, wherein the brake is housed, in particular surrounded, by the housing of the electric motor, in particular wherein the driving-off shaft of the gear is connected to a sprocket in a rotationally fixed manner, in particular wherein a chain stop device detachably connected to a chain is fastened to the housing of the electric motor, wherein the chain partially wraps around the sprocket.It is advantageous here that the brake is housed in the motor housing, although the motor housing in particular dissipates the forces for a chain stop device driven by the geared motor and is exposed to vibration oscillations which can generate strong oscillations in the case of a chain drive.In an advantageous embodiment, the brake functions as a holding brake for the rotor shaft, in particular when the chain driven by the geared motor is being tensioned or re-tensioned. It is advantageous here that the chain is held on the one hand by the chain stop device and on the other hand by means of the brake and the sprocket, so that chain links can be repaired and / or replaced even though the chain is under load.In an advantageous embodiment, the brake has a magnetic body which has an annular depression, into which an electrically energizable ring winding is inserted, in particular wherein the ring axis of the ring winding is aligned coaxially with the axis of rotation of the rotor shaft, wherein the rotor shaft has an external toothing or is connected in a rotationally fixed manner, in particular by means of a feather key connection, to an annular driver having an external toothing which is plugged onto the rotor shaft, wherein a disk-shaped brake lining carrier is plugged onto the driver and is engaged with the external toothing of the driver with its internal toothing, in particular such that the brake lining carrier is arranged displaceably in the axial direction, wherein an armature disk is arranged in the axial direction, in particular thus in the direction of the axis of rotation of the rotor shaft between the brake lining carrier and the magnetic body, said armature disk being connected in a rotationally fixed manner to the magnetic body and being arranged displaceably in the axial direction, in particular in that fastened to the magnetic body, In particular, axially oriented bolts project through recesses in the armature disk, in particular wherein, when the ring winding is energized, the armature disk is pulled toward the magnet body counter to the spring force generated by spring elements supported on the magnet body and pressing on the armature disk, so that the brake lining carrier runs free, in particular wherein, when the ring winding is not energized, the spring elements press the armature disk onto the brake lining carrier and thus the brake lining carrier is pressed on its side facing away from the magnet body onto a brake surface which is formed on a flange part or on a sheet metal part which bears on the flange part or on the motor housing. It is advantageous here that the brake automatically falls in the event of a power failure. Thus, an increased safety is achieved. In addition, a release lever can be provided, with which the brake can be permanently released by locking the release lever, in particular independently of the energization or non-energization. Braking is thus prevented during normal operation. However, during maintenance or repair of the chain, the release lever can be actuated and the brake can thereby be engaged.In an advantageous embodiment, the geared motor has a gear driven by an electric motor, wherein the gear flange, which accommodates the bearings for rotatably mounting the driving shaft of the gear on the gear flange, is centered and aligned with the flange part on the motor side, in particular by a centering collar being formed on the gear flange, on which a centering collar of the flange part is placed.This has the advantage that a simple and rapid connection of the motor to the gear is made possible, wherein a very precise alignment and centering can be achieved by the centering means. In addition, the externally toothed rotor shaft of the electric motor can be inserted into the internal toothing of the driving shaft of the transmission, so that a connection with low forces or even free of forces is made possible.In an advantageous embodiment, a torque support region and an output flange are formed on the transmission housing, in particular integrally, wherein struts and a central strut each connect the torque support region to the output flange, wherein the output flange receives a bearing of the output shaft of the transmission. It is advantageous here that despite high vibration oscillations, a reinforced transmission of the reactive moment is made possible. Although the torque support region can be formed integrally on the transmission housing, the struts connecting to the output flange nevertheless allow improved supply of the reactive forces directly from the output flange to the torque support region.In an advantageous embodiment, a cross strut connects the central strut to the struts. It is advantageous here that stiffening can be carried out simply and cost-effectively, in particular by means of forming the casting.In an advantageous embodiment, the central strut is oriented parallel to the axis of rotation of the rotor shaft. It is advantageous here that the torque support region does not require any additional axial structural length.In an advantageous embodiment, the braces each have a non-disappearing angle value relative to the center brace, in particular have the same angle value in terms of amount with mutually different signs. It is advantageous here that improved stiffening can be achieved.In an advantageous embodiment, the central strut is arranged in the plane spanned by the struts. It is advantageous here that little installation space is necessary.In an advantageous embodiment, the cross strut is arranged in the plane spanned by the struts. It is advantageous here that little installation space is necessary.In an advantageous embodiment, the distance of the struts from one another increases with increasing distance from the output flange, in particular increases strictly monotonically. This has the advantage that an effective stiffening can be achieved without an unnecessarily large amount of installation space being required.In an advantageous embodiment, the axial width of the torque support region, i.e. in particular the width of the torque support region measured in a direction parallel to the direction of the axis of rotation of the rotor shaft, decreases monotonically with increasing distance from the central strut. It is advantageous here that the torque support region can be made compact.In an advantageous embodiment, springs connect two regions of the transmission housing spaced apart from one another in the axial direction. It is advantageous here that, despite the vibration oscillations introduced by the conveyor chain via a sprocket, the gear is sufficiently stiff and oscillations can be suppressed.It is also advantageous in the subject matter of the invention that a rapid and simple replacement of the chain links can be ensured with high working safety. This is because no particular effort is required. Only the release lever and the chain stop device need be provided suitably.However, since the chain stop device is attached to the geared motor, i.e. to a housing-forming part of the geared motor, no particular additional outlay is necessary and nevertheless an efficient dissipation of the chain forces is made possible. This is because during the replacement of the chain links, the chain force must be conducted through the geared motor from the chain stop device to the sprocket.In an advantageous embodiment, the chain stop device is fastened to the geared motor. It is advantageous here that the chain force in the geared motor can be conducted directly to the sprocket wheel.In an advantageous embodiment, the geared motor has an electric motor, the housing of which houses and / or surrounds the brake. It is advantageous here that the brake does not require a separate housing and thus only a small amount of effort is required for housing the brake.In an advantageous embodiment, the sprocket engages in the chain over a circumferential angle range of more than 90°, in particular and less than 180°. The circumferential angle range is relative to the rotational axis of the sprocket. It is advantageous here that the chain is securely held.In an advantageous embodiment, in the third method step, the torque transmitted from the sprocket to the chain is controlled to a setpoint value, in particular to achieve a setpoint value for the chain tension. It is advantageous here that the chain can be repaired under full load. This is because the provided chain tension can be introduced by means of the geared motor.In an advantageous embodiment, the first rotational speed threshold value is less than, in particular at least ten times less than, the setpoint rotational speed. It is advantageous here that during slow travel the chain tension can be adjusted precisely without overloading the chain. This is because the torque of the geared motor can be directly regulated by a converter feeding the electric motor to a setpoint value.In an advantageous embodiment, in the fourth method step, the brake, in particular the ring winding of the brake, is switched substantially without current. It is advantageous here that increased safety can be achieved by the brake being switched off from current on the one hand and thereby being engaged. In addition, the release lever is brought into the corresponding rotational position for the brake to be engaged. In the de-energized state of the brake, the toroidal coil is essentially or completely de-energized, but the signal electronics of the brake must nevertheless remain electrically powered-in particular for supplying the sensors and their evaluation circuits. In an advantageous embodiment, the brake has a magnetic body which has an annular depression, into which an electrically energizable ring winding is inserted, in particular wherein the ring axis of the ring winding is aligned coaxially with the axis of rotation of the rotor shaft, wherein the rotor shaft has an external toothing or is connected in a rotationally fixed manner in particular by means of a feather key connection to an annular externally toothed driver which is plugged onto the rotor shaft, wherein a disk-shaped brake lining carrier is plugged onto the driver and is engaged with the external toothing of the driver by its internal toothing, in particular such that the brake lining carrier is arranged displaceably in the axial direction, wherein an armature disk is arranged in the axial direction between the brake lining carrier and the magnetic body, said armature disk being connected in a rotationally fixed manner to the magnetic body and being arranged displaceably in the axial direction, wherein, when the annular winding is energized, the armature disk is pulled toward the magnetic body counter to the spring force generated by spring elements supported on the magnetic body and pressing on the armature disk, so that the brake lining carrier runs free, in particular wherein, when the annular winding is not energized, the spring elements press the armature disk onto the brake lining carrier and thus the brake lining carrier is pressed on its side facing away from the magnetic body onto a braking surface which is formed on a flange part or on a sheet metal part which bears against the flange part or on the motor housing.It is advantageous here that the brake automatically falls in the event of a power failure, i.e. automatically changes over into the safe state.In an advantageous embodiment, the release lever is connected via a pivot joint to a bolt arranged to be axially movable, wherein the release lever is supported on a pivot point which is arranged on a flange part or bearing flange of the electric motor, wherein the bolt projects through the magnet body and through a recess of the armature disk and is formed widened on the side of the armature disk facing away from the magnet body or is connected to a part for widening such that the bolt is axially delimited by means of the widening. It is advantageous in this case that manual venting is made possible. In particular, the release lever can be brought into a rotational position in which the brake is released.In an advantageous embodiment, the release lever can be locked by a locking device of the brake, in particular on the magnetic body. It is advantageous here that the safe state of the brake can be fixed.In an advantageous embodiment, the housing of the electric motor, which housing is in particular embodied in multiple parts, houses not only the stator of the electric motor but also the brake, in particular wherein the release lever protrudes through the housing into the environment of the electric motor. It is advantageous here that the release lever can be detachably connected to the housing, i.e. in particular locked.In an advantageous embodiment, the brake is arranged on the axial end region of the rotor shaft of the electric motor facing away from the gear mechanism. It is advantageous here that sufficient free space is present for the actuation of the release lever.In an advantageous embodiment, springs connect a first region of the transmission housing to a second region of the transmission housing, in particular wherein the first region is spaced apart from the second region in the axial direction, in particular parallel to the direction of the axis of rotation of the rotor shaft, in particular wherein the springs are arranged on the outer side of the transmission housing. It is advantageous here that, despite the high forces transmitted through the housing, the housing can be stabilized and sufficient rigidity of the housing can be maintained. In particular, oscillations of the housing can be suppressed.Important features in the chain conveying device for carrying out an aforementioned method are that the chain conveying device has the sprocket wheel which can be driven by a geared motor and engages in the chain which is detachably connected to a chain stopping device, wherein the chain stopping device is connected to the housing of the geared motor, wherein the chain conveying device has a regulating device for setting the chain tension of the chain by regulating the torque output by the geared motor via the sprocket wheel to the chain, in particular wherein the geared motor can be controlled or regulated by a converter supplying the electric motor of the geared motor in such a way that the chain tension of the chain can be tensioned to a setpoint value by controlling or regulating the torque.It is advantageous here that the chain conveying device is designed to ensure repair of the chain with simultaneously high safety. For this purpose, the chain stop device can be fastened to the geared motor and the sprocket wheel is able to absorb the chain tension and to hold the chain via the transmission by means of the holding brake arranged on the rotor shaft of the electric motor driving the transmission.Further advantages are evident from the dependent claims. The invention is not limited to the combination of features of the claims. The skilled person will be familiar with further meaningful combination possibilities of claims and / or individual claim features and / or features of the description and / or of the figures, in particular from the task and / or the task which arises by comparison with the prior art.The invention will now be explained in more detail with reference to schematic figures:FIG. 1 schematically shows a chain conveying device according to the invention with a geared motor.In FIG. 2, the geared motor is shown in a sectional side view.FIG. 3 shows the geared motor in a side view.In FIG. 4, the geared motor is shown in an oblique view.As shown in the figures, the chain device comprises a geared motor whose output shaft 3 drives a sprocket wheel 2, whose teeth engage recesses of chain links of a chain 1 and which thus drives the chain 1.Preferably, the chain 1 has a length of more than 20 metres and is used in mining or mining equipment for conveying rock, ore or coal.The geared motor comprises an electric motor 30 driving a gear 31, the output shaft of which acts as output shaft 3 of the geared motor.At the end of the rotor shaft of the electric motor 30 axially facing away from the gear, an electromagnetically actuatable brake is arranged, which acts as a holding brake for the rotor shaft 24 when the tensioning or re-tensioning of the chain 1 is to be carried out.To ensure operation, the brake can additionally be released manually. For this purpose, an air lever 29 is provided, with which the brake remains aired independently of the energization or non-energization of its coil.The brake has a magnetic body 28 which is made of a ferromagnetic material and has an annular depression, the ring axis of which is aligned coaxially with the axis of rotation of the rotor shaft and which is open toward the transmission.A ring winding that can be supplied with current is inserted into the ring-shaped depression of the magnetic body 28 and is sealed and cast with casting compound.A ring-shaped driver is plugged onto the rotor shaft, which driver has an external toothing which is in engagement with an internal toothing of a brake lining carrier 26, which is plugged onto the driver. The driver is connected to the rotor shaft preferably in a rotationally fixed manner by means of a feather key connection. The brake lining carrier 26 is arranged displaceably in the axial direction on the driver.An armature disk 27 is made of ferromagnetic material and is arranged axially between the brake lining carrier 26 and the magnetic body 28.When the annular winding is energized, the armature disk 27, which is arranged in a rotationally fixed manner but axially displaceably with respect to the magnetic body 28, in particular in that bolts fastened in the magnetic body 28 project through recesses in the armature disk 27, is pulled toward the magnetic body 28 counter to the spring force generated by spring elements supported in the magnetic body 28. When the annular winding is not energized, the spring elements press the armature disk 27 onto the brake lining carrier 26, so that this brake lining carrier 26 is pressed on its side facing away from the armature disk 27 onto a braking surface which is formed on the bearing flange or on a part connected to the bearing flange.The release lever 29 is mounted pivotably with respect to a pivot point on the magnetic body 28 or on a part connected to the magnetic body 28, so that during its rotational movement it makes a bolt linearly movable in the axial direction.The bolt projects through a recess of the magnet body 28 and through a recess of the armature disk 27. the bolt is widened on the side of the armature disk 27 facing away from the magnet body 28 and therefore draws the armature disk 27 toward the magnet body 28 upon actuation of the release lever, wherein upon actuation of the release lever 29 the spring force generated by the spring elements is overcome, even if the annular winding is not energized. Manual venting is thus made possible. The brake can only be engaged when the armature disk 27 is released by a corresponding rotational position of the release lever 29. This is because, when the release lever 29 is rotated, the bolt is moved in the axial direction and the armature disk 27 is forced toward the magnetic body 28.For this purpose, the bolt is widened at its end region facing away from the magnetic body 28, in particular so that the bolt rests with this widened end region against the armature disk 27 and does not slide through the recess of the armature disk 27.Before the tensioning or re-tensioning of the chain 1 is carried out, the geared motor is firstly switched off, that is to say the chain 1 is brought to zero speed.Thereafter, by means of a chain stop device 4, the chain 1 is detachably connected at one of its chain links to a stationary part of the system, so that the chain 1 cannot move any further here. Preferably, the chain stop device 4 is attached to the geared motor, in particular between the gear and the motor, so that the chain 1 is stopped by means of the chain stop device 4 and is detachably connected to the housing of the geared motor.After stopping the geared motor and stopping the chain 1, the brake is activated. This is effected on the one hand by actuating the release lever 29 and additionally de-energizing the coil of the brake. As a result, the brake falls and thus prevents the rotational movement of the rotor shaft, which therefore also stops the rotational movement of the output shaft 3 of the transmission 31 via the transmission 31.In this way, the chain 1 is repairable between the sprocket 2 and the chain stopper 4. For example, an exchange, i.e. replacement, of chain links of the chain 1 is made possible in this region even if the remaining region of the chain 1 is under load.The chain tension can thus be adjusted.After the chain links have been installed, the chain 1 can be fully inserted again. Thus, the chain stop device 4 is then released from the chain 1 and thus the chain 1 is then released and the brake is also released by energizing the coil of the brake and actuating the release lever 29 29.The electric motor is flange-mounted directly on the transmission and is centered in the process. By means of this direct centering of the flange, a coupling can be saved and the overall length is thus shortened. The flange centering makes it possible that only the transmission-side transmission flange 22 has to be designed with the corresponding centering means, and no further adaptations are necessary on the engine side.Due to the externally toothed rotor shaft, which only has to be inserted into the internal toothing of the driving shaft of the transmission when connecting the motor to the transmission, a force-free or at least low-force flange-mounting of the motor to the transmission is made possible.The transmission flange 22 is additionally stabilized by casting a torque support region 40 onto the transmission flange 22, i.e. in particular the transmission flange 22 is embodied as one piece with the torque support region 40. This torque support region 40 is connected via struts 21 and a central strut 41 arranged between the struts 21 to the output flange of the transmission, which receives a bearing of the output shaft of the transmission.The central strut 41 is oriented parallel to the axis of rotation of the rotor shaft of the electric motor. The struts 21 are oriented at an angle to the central strut 41, in particular wherein they therefore have a non-disappearing angle to the central strut 41.Although the angles of the struts 21 to the central strut 41 are identical in magnitude, they have a different sign.The struts 21 span a plane in which the central strut 41 is also located.The end regions of the struts 21 and of the central strut 41 facing the electric motor are connected by means of the torque support region 40. The other end regions open into the output flange which receives the bearing for rotatably mounting the output shaft.A cross strut, which is arranged axially, i.e. in the direction of the axis of rotation of the rotor shaft of the electric motor, between the torque support region 40 and the output flange, connects the struts 21 to the central strut 41.Thus, the torque support, in particular the torque support region 40, is rigidly connected to the output flange.For further stiffening and / or suppression of resonances, the springs 32 are provided, which connect two regions spaced apart from one another in the axial direction.The rotor shaft 24 is rotatably supported via a bearing that is accommodated in the bearing flange 25.In further embodiments according to the invention, the chain stop device 4 is mounted at a different position, so that a longer length of the chain is replaceable between the sprocket 2 and the chain stop device 4.In further embodiments according to the invention, it is also possible, after attachment of the chain stop device 4, to initially operate the geared motor at a very low speed in order to tension the chain 1 in the conveying region and only then to activate the brake in order to maintain the chain tension thus achieved, while the chain link or links are replaced and / or exchanged in the region of the chain 1 between the chain stop device 4 and the sprocket 2.The brake is arranged in the motor housing. Thus, the brake is surrounded and protected by the motor housing.The driving shaft 20 of the transmission has an external toothing on its end region facing the electric motor and / or the brake, with which the driving shaft 20 is inserted into an internal toothing of the rotor shaft 24. A high torque can thus be transmitted and an alignment error of the shaft 20 with respect to the rotor shaft 24 can be compensated. For this purpose, the teeth of the internal toothing and / or the teeth of the external toothing are preferably designed to be spherical.In order to align the axes of rotation of the driving shaft 20 as exactly as possible with the axis of rotation of the rotor shaft 24 when the electric motor 30 is connected to the gear 31, the gear flange 22, which accommodates the bearings for rotatably mounting the driving shaft on the gear flange, is centered and aligned with the motor flange, that is to say a flange part 23, by a centering collar being formed on the gear flange 22, on which a centering collar of the flange part 23 is placed. In this way, highly accurate alignment is made possible. The toothed coupling formed from the internal toothing and external toothing compensates for residual tolerances.As shown in FIG. 2, springs 32 attached to the gear unit connect two regions of the housing of the gear unit 31 spaced apart from one another in the axial direction, in particular in the direction of the axis of rotation of the rotor shaft of the electric motor 30, and resonance oscillations can be suppressed in this way and the stability and rigidity of the gear unit 31 are designed to be increased.In a circumferential angle range of more than 90°, in particular and less than 180°, in particular with respect to the axis of rotation of the sprocket 2, the sprocket 2 engages in the chain 1. Thus, even when the chain region is tensioned, the chain link to be replaced can be released.List of reference characters1 Chain 2 Sprocket 3 Driving shaft 4 Chain stop device 20 Driving shaft 21 Strut 22 Transmission flange 23 Flange part, motor-side 24 Rotor shaft 25 Bearing flange 26 Brake lining carrier, disk-shaped 27 Armature disk 28 Magnetic body 29 Release lever 30 Electric motor 31 Transmission 32 Springs 40 Torque support region 41 Central strut

Claims

Geared motor, in particular for a chain conveying device, wherein the geared motor has a gear driven by an electric motor, wherein an electromagnetically actuatable brake is arranged on the end of the rotor shaft of the electric motor facing away from the gear axially, in particular in a direction parallel to the axis of rotation of the rotor shaft of the electric motor, wherein the brake is housed, in particular surrounded, by the housing of the electric motor, wherein in particular the driving shaft of the gear is connected to a sprocket in a rotationally fixed manner, in particular wherein a chain stop device detachably connected to a chain is fastened to the housing of the electric motor, wherein the chain partially wraps around the sprocket.Geared motor according to claim 1, characterised in that the brake acts as a retaining brake for the rotor shaft, in particular when performing the tensioning or re-tensioning of the chain driven by the geared motor.Geared motor according to one of the preceding claims, characterized in that the brake has a magnetic body which has an annular depression, into which an electrically energizable annular winding is inserted, in particular wherein the annular axis of the annular winding is aligned coaxially with the axis of rotation of the rotor shaft, wherein the rotor shaft has an external toothing or is connected in a rotationally fixed manner, in particular by means of a feather key connection, to an annular driver which has an external toothing and is plugged onto the rotor shaft, wherein a disc-shaped brake lining carrier is plugged onto the driver and is in engagement with the external toothing of the driver with its internal toothing, in particular such that the brake lining carrier is arranged displaceably in the axial direction, wherein an armature disc is arranged in the axial direction, in particular therefore in the direction of the axis of rotation of the rotor shaft between the brake lining carrier and the magnetic body, said armature disc being connected in a rotationally fixed manner to the magnetic body and being arranged displaceably in the axial direction, In particular, in that bolts fastened to the magnetic body, in particular aligned axially, project through recesses in the armature disc, in particular wherein, when the ring winding is energized, the armature disc is pulled towards the magnetic body counter to the spring force generated by spring elements supported on the magnetic body and pressing on the armature disc, so that the brake lining carrier runs free, in particular wherein, when the ring winding is not energized, the spring elements press the armature disc on the brake lining carrier and thus the brake lining carrier is pressed on its side facing away from the magnetic body on a brake surface which is formed on a flange part or on a sheet metal part which bears on the flange part or on the motor housing.Geared motor according to one of the preceding claims, characterized in that the gear flange (22), which accommodates the bearings for rotatably mounting the driving shaft (20) of the gear on the gear flange (22), is centered and aligned with the flange part (23) on the motor side, in particular in that a centering collar is formed on the gear flange (22), on which a centering collar of the flange part (23) is placed.Geared motor according to one of the preceding claims, characterized in that a torque support region and a driven flange are formed on the gear housing, in particular in one piece, wherein struts (21) and a central strut (41) each connect the torque support region to the driven flange, wherein the driven flange accommodates a bearing of the driving shaft of the gear.Geared motor according to one of the preceding claims, characterized in that a transverse strut connects the central strut (41) to the struts (21).Geared motor according to one of the preceding claims, characterized in that the central strut (41) is oriented parallel to the axis of rotation of the rotor shaft, and / or in that the struts (21) each have a non-disappearing angle value with respect to the central strut, in particular have the same angle value in terms of amount with mutually different signs.Geared motor according to one of the preceding claims, characterized in that the central strut is arranged in the plane spanned by the struts (21).Geared motor according to one of the preceding claims, characterized in that the transverse strut is arranged in the plane spanned by the struts (21).Geared motor according to one of the preceding claims, characterized in that the distance between the struts (21) increases with increasing distance from the output flange, in particular increases strictly monotonically.Geared motor according to one of the preceding claims, characterized in that the axial width of the torque support region, in particular therefore the width of the torque support region measured in the direction parallel to the direction of the axis of rotation of the rotor shaft, decreases monotonically with increasing distance from the central strut.Geared motor according to one of the preceding claims, characterized in that springs connect two regions of the gear housing which are spaced apart from one another in the axial direction to one another.Chain conveying device, wherein the chain conveying device comprises a chain, a sprocket and a geared motor according to one of the preceding claims, wherein the electric motor of the geared motor comprises an electromagnetically actuatable brake on its side facing away from the gear of the geared motor, wherein the sprocket is connected in particular in a positively locking manner to a driving shaft of the geared motor, wherein teeth of the sprocket engage in chain links of the chain, in particular for conveying and holding the chain, wherein the brake is housed, in particular surrounded, by the housing of the electric motor, in particular wherein the driving shaft of the gear is connected in a rotationally fixed manner to a sprocket, in particular wherein a chain stop device detachably connected to a chain is fastened to the housing of the electric motor, wherein the chain partially wraps around the sprocket, in particular wherein, on the chain driven axially by the gear, the chain is connected to the driving shaft of the geared motor, in particular, the electromagnetically actuatable brake is arranged on the end of the rotor shaft of the electric motor facing away from the axis of rotation of the rotor shaft of the electric motor in a direction parallel to the axis of rotation of the rotor shaft of the electric motor.Chain conveying device according to one of the preceding claims, characterized in that the chain stopping device is fastened to the geared motor and / or in that the chain is fixed to a first of its chain links by means of a chain stopping device, wherein the chain stopping device is fastened to the geared motor.Chain conveying device according to one of the preceding claims, characterized in that the geared motor has an electric motor, the housing of which houses and / or surrounds the brake.Chain conveying device according to one of the preceding claims, characterized in that the chain wheel engages in the chain over a circumferential angle range of more than 90°, in particular and less than 180°, in the chain, and / or in that the release lever is connected via a pivot joint to a bolt arranged to be axially movable, and / or in that the release lever is supported on a pivot point which is arranged on a flange part or bearing flange of the electric motor, wherein the bolt projects through the magnetic body and through a recess of the armature disc and is formed widened on the side of the armature disc facing away from the magnetic body or is connected to a part for widening such that the bolt is axially delimited by means of the widening, and / or in that the release lever can be locked by a locking device of the brake, in particular on the magnetic body, and / or that the housing of the electric motor, which housing is in particular embodied in multiple parts, encloses not only the stator of the electric motor but also the brake, in particular wherein the air lever projects through the housing into the environment of the electric motor, and / or that the brake is arranged on the axial end region of the rotor shaft of the electric motor facing away from the transmission, and / or that springs connect a first region of the transmission housing to a second region of the transmission housing, in particular wherein the first region is spaced apart from the second region in the axial direction, in particular parallel to the direction of the axis of rotation of the rotor shaft, in particular wherein the springs are arranged on the outer side of the transmission housing.

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