Geared motor with a brake

Abstract

The invention relates to a geared motor with a brake, wherein the geared motor comprises a transmission, wherein the transmission has a first housing, wherein the brake has a second housing, wherein a rotatably mounted intermediate shaft of the transmission projects through the first housing, wherein a braking torque can be introduced into the intermediate shaft by the brake.

Description

[0001] Gear motor with brake

[0002] Description:

[0003] The invention relates to a geared motor with brake.

[0004] It is generally known that a geared motor has a gearbox that can be driven by an electric motor.

[0005] From DE 10 2020207 403 A1, the closest prior art is a drive unit for an industrial truck.

[0006] An electromechanical drive device with emergency device is known from DE 691 10 745 T2.

[0007] A brake is known from DE 10 2010 049 744 A1.

[0008] From DE 10 2010 049 747 A1 a kit for the production of different electric motors of a series of electric motors is known.

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

[0010] The invention is therefore based on the object of developing a transmission in which high dynamics can be achieved.

[0011] According to the invention, the object is achieved in the transmission according to the features specified in claim 1.

[0012] Important features of the invention in the geared motor with brake are that the geared motor has a gearbox, wherein the gearbox has a first housing, wherein the brake has a second housing, wherein a rotatably mounted intermediate shaft of the gearbox projects through the first housing, wherein a braking torque can be introduced into the intermediate shaft from the brake.

[0013] The advantage here is that a high braking torque can be applied by the brake. This allows for high dynamic performance, particularly due to the high braking acceleration. Furthermore, not only can the electric motor be configured as a brake motor, but a brake can also be installed on the intermediate shaft. This allows for increased braking torque, allowing braking to be performed even if the brake motor fails.

[0014] In an advantageous embodiment, the transmission has two or more stages. It is advantageous that an intermediate shaft can be provided.

[0015] In an advantageous embodiment, a first gear part is rotationally fixedly connected to the input shaft of the transmission and engages with a second gear part, wherein the second gear part is rotationally fixedly connected to the intermediate shaft and engages with a third gear part, wherein the third gear part is rotationally fixedly connected to the output shaft of the transmission. It is advantageous that the transmission has an intermediate shaft, and thus the brake is operatively connected to the output shaft not directly, but via a gear stage.

[0016] In an advantageous embodiment, a brake motor, in particular an electric motor having an additional brake, drives the input shaft of the gearbox, in particular wherein the brake of the brake motor and the brake of the geared motor acting on the intermediate shaft are identical in construction or at least have identical brake pad carriers, identical armature disks, identical toroidal windings, identical spring elements and / or identical magnetic bodies. The advantage here is that a high variety of geared motors with or without a brake acting on the intermediate shaft can be provided with a small number of parts. This is because the electric motor of the geared motor driving the gearbox can be designed either with or without an additional brake. Furthermore, the nominal torque of the two brakes is the same, so that the brake of the electric motor can be oversized.In this way, low wear and tear can be achieved and thus high safety.

[0017] In addition, the two brakes can then be arranged on two different sides of the gearbox, so that the frictional heat of the brakes can be dissipated to the environment without interference.

[0018] In an advantageous embodiment, the first housing has a lower part to which a cover part of the first housing is connected. This is advantageous because the gear unit is composed of two parts, thus allowing for easy assembly.

[0019] In an advantageous embodiment, the second housing is connected to the first housing in a rotationally fixed manner by means of a torque arm. This is advantageous in that a higher braking torque can be achieved, since the torque arm can dissipate a higher braking torque thanks to its eccentric shape.

[0020] In an advantageous embodiment, the brake has a shaft, in particular a rotatably mounted shaft, a driver and a brake pad carrier, wherein the driver has external teeth and is connected to the shaft in a rotationally fixed manner, in particular by means of a keyway connection, wherein the shaft is connected to the intermediate shaft in a rotationally fixed manner or the shaft is designed in one piece and / or in one part with the intermediate shaft, in particular wherein the shaft and the intermediate shaft are aligned coaxially to one another, in particular wherein the axis of rotation of the shaft and the axis of rotation of the intermediate shaft are aligned coaxially to one another, wherein the brake pad carrier has internal teeth, wherein the brake pad carrier is placed on the driver and the internal teeth are in engagement with the external teeth, in particular so that the brake pad carrier is connected to the driver in a rotationally fixed manner and is axially displaceable, in particular thus parallel to the direction of the axis of rotation of the shaft.The advantage is that in the event of a power failure, the brake is automatically applied, thus further increasing safety.

[0021] In an advantageous embodiment, a magnetic body of the brake is connected to the second housing or forms part of the second housing, wherein a ring winding is accommodated in a particularly annular recess of the magnetic body, wherein a ferromagnetic armature disk is connected to the magnetic body in a rotationally fixed manner and is arranged axially, in particular parallel to the axis of rotation of the shaft, displaceably relative to the magnetic body, wherein the armature disk is arranged axially between the brake pad carrier and the magnetic body, wherein spring elements supported on the magnetic body press on the armature disk, in particular in such a way that when the ring winding is energized, the armature disk is drawn towards the magnetic body and when the armature disk is not energized, the armature disk presses the brake pad carrier onto a braking surface formed on a part connected to the second housing, in particular a flat and finely machined surface.The advantage here is that the brake needs to be manufactured simply and cost-effectively.

[0022] In an advantageous embodiment, a torque arm is detachably and / or rotationally fixedly connected to the first housing, in particular with spacer bolts arranged between the torque arm and the first housing, with the second housing being detachably and / or rotationally fixedly connected to the torque arm. The advantage here is that the torque arm is easily connectable and is optionally provided on the housing, thus not having to be present in another variant of the geared motor, especially like the brake.

[0023] In particular, the center axes of the spacer bolts lie in a plane whose normal is perpendicular to the rotational axis of the electric motor's rotor shaft, particularly with two spacer bolts. This is advantageous because the torque support is spatially stabilized, allowing the dissipation of a positive torque as well as a negative torque.

[0024] In an advantageous embodiment, the spacer bolts are designed as hollow cylinders, with first screws protruding through the spacer bolts, through the torque arm and through the second housing and being screwed with their respective threaded area into a respective axial bore of the first housing, in particular of the cover part, with the respective screw head of the respective first screw pressing the second housing towards the torque arm, in particular and thus the spacer bolts being pressed towards the first housing. The advantage here is that the spacer bolts can be provided in a simple manner and a fixed distance can be guaranteed by means of the screws which protrude through the spacer bolts. In this way, the heat from the brake can be dissipated efficiently because the torque arm increases the heat capacity of the brake housing.In addition, an effective thermal barrier between the first housing and the torque arm can be achieved, especially if the spacer bolts are made of plastic.

[0025] In another advantageous embodiment, the spacer bolts are designed as hollow cylinders, wherein first screws protrude through the spacer bolts, through the torque support and are screwed with their respective threaded area into a respective axial bore of the first housing, in particular of the cover part, wherein the respective screw head of the respective first screw presses the torque support towards the spacer bolts, in particular the spacer bolts are thus pressed towards the first housing, in particular wherein the second housing is pressed onto the torque support by means of second screws, wherein the second screws are screwed with their threaded area into threaded bores of the torque support. The advantage here is that a thermal barrier can be realized by means of the spacer bolts.

[0026] In an advantageous embodiment, the torque arm is designed eccentrically, in particular so that the radial distance from the axis of rotation of the intermediate shaft is variable and / or has different values ​​as a function of the circumferential angle, particularly relative to this axis of rotation. This is advantageous in that a larger radial distance can be used to attach the torque arm, thus deriving a higher reaction braking torque.

[0027] In an advantageous embodiment, the torque arm is attached to the first housing, in particular to the cover part of the first housing, by means of the first screws, wherein at least two first screws have a smaller radial distance from the axis of rotation of the intermediate shaft than a third of the first screws. The advantage here is that the eccentric design of the torque arm allows for a larger radial distance, thus allowing for a higher reaction torque to be dissipated.

[0028] In an advantageous embodiment, a first bearing, in particular a roller bearing, is accommodated in the cover part for rotatably supporting the intermediate shaft, while a second bearing, in particular a roller bearing, is accommodated in the lower part for rotatably supporting the intermediate shaft. This is advantageous in that a split bearing arrangement is possible. This allows for a large distance between the bearings, thus dissipating a high transverse moment. However, this requires the cover part to be centered relative to the lower part using highly precise centering means, in particular, such as a finely machined centering collar formed on the cover part.In an advantageous embodiment, a first and a second bearing are arranged in the transmission for rotatably supporting the intermediate shaft. An inner ring of the first bearing is mounted on the intermediate shaft, and an outer ring of the first bearing is housed in the cover part. An inner ring of the second bearing is mounted on the intermediate shaft, and an outer ring of the second bearing is housed in the lower part. This allows for simple manufacturing.

[0029] In an advantageous embodiment, the torque arm is shaped eccentrically and / or the first, in particular at least one, screw which has the greatest radial distance from the axis of rotation of the intermediate shaft has a smaller radial distance from the axis of rotation of the input shaft than from the axis of rotation of the intermediate shaft. The advantage here is that a large radial distance can be achieved and thus a high reaction torque can be transmitted. In addition, the eccentric design seen from the axis of rotation of the intermediate shaft reduces the space required, although then only a few screws can be arranged over this large radial distance. This is because the area of ​​the torque arm with the maximum radial distance only covers a circumferential angular range, but not the entire circumference, in particular not 360°.

[0030] In an advantageous embodiment, the input shaft is aligned parallel to the intermediate shaft. This allows the transmission to be designed as a parallel-shaft transmission.

[0031] Further advantages emerge from the dependent claims. The invention is not limited to the combination of features in the claims. Further possible combinations of claims and / or individual claim features and / or features of the description and / or the figures will become apparent to those skilled in the art, particularly from the problem and / or the problem posed by comparison with the prior art. The invention will now be explained in more detail with reference to schematic illustrations:

[0032] Figure 1 shows a side view of a geared motor with brake 1 according to the invention.

[0033] Figure 2 shows an oblique view of the geared motor with brake 1 removed.

[0034] Figure 3 shows a side view of the partially cut-away gear motor.

[0035] As shown in the figures, the geared motor has a gear driven by an electric motor 4, the housing of which has a lower part 3 and a cover part 2 connected to the lower part 3.

[0036] The rotor shaft of the electric motor 4 is connected in a rotationally fixed manner to a first toothed part of the gear, which is in engagement with a second toothed part, which is connected in a rotationally fixed manner to an intermediate shaft 30 rotatably mounted in the housing of the geared motor.

[0037] A third toothed part engages with a fourth toothed part, which is preferably connected in a rotationally fixed manner to the output shaft of the gearbox.

[0038] The axis of rotation of the intermediate shaft 30 is spaced from the axis of rotation of the rotor shaft, these two axes of rotation being arranged parallel to each other.

[0039] The intermediate shaft 30 projects through a recess in the cover part 2 and is actuated by the brake 1, in particular which is designed as an electromagnetically actuated brake.

[0040] The bearing of the intermediate shaft 30 is designed in a split manner: a first bearing for the rotatable bearing of the intermediate shaft 30 is accommodated in the lower part 3 and a second bearing for the rotatable bearing of the intermediate shaft 30 is accommodated in the cover part 2.

[0041] The brake housing is connected to a flat torque arm 6, in particular by means of screws. The torque arm 6 is spaced from the cover part 2 by means of spacer bolts 5 arranged between the cover part 2 and the torque arm 6. The screws are preferably guided through the spacer bolts, i.e., protrude through them, and are screwed with their respective threaded areas into threaded holes in the cover part 2. The screw heads of the screws press the housing of the brake 1, on the side of the housing of the brake 1 facing away from the cover part 2 and the torque arm 6, toward the cover part 2 or the torque arm 6.

[0042] The torque arm 6 is eccentrically shaped. Thus, the hole pattern for accommodating the screws is not concentric with the rotational axis of the intermediate shaft 30, but eccentric. This allows a high reaction torque of the brake 1 to be dissipated.

[0043] In particular, the screws are arranged at different radial distances from the axis of rotation of the intermediate shaft 30.

[0044] On its side facing the cover part 2, the torque support 6 has an axially projecting centering collar formed on the torque support 6, which rests against a bore in the cover part 2 that passes through the cover part 2. This enables centering of the torque support 6 in a simple and highly precise manner.

[0045] Brake 1 is designed as an electromagnetically actuated brake.

[0046] For this purpose, the brake 1 has a magnetic body that is connected to the brake housing or forms part of the housing. The magnetic body is preferably made of a ferromagnetic material, in particular spheroidal cast iron.

[0047] The magnetic body has an annular recess in which an electrically energizable ring winding is accommodated, which is preferably aligned concentrically to the intermediate shaft.

[0048] A ring-shaped driver is mounted on the intermediate shaft or a shaft connected to the intermediate shaft 30 for rotational stability and is connected to the shaft or intermediate shaft 30 for rotational stability. The driver has external teeth. A disc-like brake pad carrier is mounted on the driver, which has internal teeth that mesh with the external teeth. Thus, the brake pad carrier is axially displaceable, in particular parallel to the rotational axis of the intermediate shaft, and is connected to the intermediate shaft for rotational stability.

[0049] A ferromagnetic armature disk is arranged axially between the brake pad carrier and the magnet body and is connected to the magnet body in a rotationally fixed manner, whereby the armature disk is axially displaceable.

[0050] For this purpose, bolts are particularly firmly connected to the magnetic body, which protrude through recesses in the armature disk, so that the armature disk is connected to the magnetic body in a rotationally fixed manner.

[0051] On the side of the brake pad carrier facing away from the armature disc, a braking surface is formed, in particular on a part that is connected in a rotationally fixed manner to the brake housing.

[0052] Spring elements supported on the magnet body press against the armature disk, exerting a spring force directed toward the brake pad carrier. This releases the brake pad carrier and releases the brake.

[0053] When the toroidal winding is energized, the armature disk is attracted to the magnet body, particularly against the spring force generated by the spring elements. When the toroidal winding is deenergized, the spring elements push the armature disk toward the brake pad carrier, pressing the brake pad carrier onto the braking surface and applying braking force to the brake pads attached to both sides of the brake pad carrier. The brake is then activated and applied.

[0054] In further embodiments according to the invention, the torque arm 6 is fastened to the cover part 2 with screws, wherein the screws also extend through the spacer bolts 5 and are screwed into the threaded holes in the cover part 2, and the housing of the brake 1 is fastened to the torque arm with second screws. Thus, the torque arm 6 remains firmly connected to the cover part 2 even when the brake 1 is replaced. In further embodiments according to the invention, the electric motor 4 itself is designed as a brake motor, so that an additional brake is arranged either on the side of the electric motor 4 facing away from the transmission or between the electric motor 4 and the transmission.

[0055] List of reference symbols

[0056] 1 Brake, in particular electromagnetically actuated brake 2 Cover part

[0057] 3 Lower part

[0058] 4 electric motor

[0059] 5 spacer bolts

[0060] 6 Torque support 30 Intermediate shaft

[0061] 31 Centering collar

Claims

Patent claims:

1. Geared motor with brake, wherein the geared motor has a gearbox, wherein the gearbox has a first housing, wherein the brake has a second housing, characterized in that a rotatably mounted intermediate shaft of the gearbox projects through the first housing, wherein a braking torque can be introduced into the intermediate shaft from the brake.

2. Geared motor according to claim 1, characterized in that the transmission is two-stage or more-stage, and / or that a first toothed part is rotatably connected to the input shaft of the transmission and is in engagement with a second toothed part, wherein the second toothed part is rotatably connected to the intermediate shaft and is in engagement with a third toothed part, wherein the third toothed part is rotatably connected to the output shaft of the transmission.

3. Geared motor according to one of the preceding claims, characterized in that a brake motor, in particular an electric motor having a further brake, drives the driving shaft of the gearbox, in particular wherein the brake of the brake motor and the brake acting on the intermediate shaft of the geared motor are identical in construction or at least have identical brake pad carriers, identical armature discs, identical ring windings, identical spring elements and / or identical magnet bodies.

4. Geared motor according to one of the preceding claims, characterized in that the first housing has a lower part to which a cover part of the first housing is connected, and / or that the second housing is rotatably connected to the first housing by means of a torque support.

5. Geared motor according to one of the preceding claims, characterized in that the brake comprises a shaft, in particular a rotatably mounted shaft, a driver and a brake pad carrier, wherein the driver has external teeth and is rotationally fixed to the shaft, in particular by means of a keyway connection, wherein the shaft is rotationally fixed to the intermediate shaft or the shaft is formed integrally and / or in one piece with the intermediate shaft, in particular wherein the shaft and the intermediate shaft are aligned coaxially to each other, in particular wherein the axis of rotation of the shaft and the axis of rotation of the intermediate shaft are aligned coaxially to each other, wherein the brake pad carrier has internal teeth, wherein the brake pad carrier is mounted on the driver and the internal teeth are in engagement with the external teeth, in particular such that the brake pad carrier is rotationally fixed to the driver and axially,in particular, it is displaceable parallel to the direction of the axis of rotation of the shaft.

6. Geared motor according to one of the preceding claims, characterized in that a magnetic body of the brake is connected to the second housing or forms a part of the second housing, wherein a ring winding is received in a particularly annular recess of the magnetic body, wherein a ferromagnetic armature disk is rotationally fixed to the magnetic body and is arranged to be axially displaceable relative to the magnetic body, in particular parallel to the axis of rotation of the shaft, wherein the armature disk is arranged axially between the brake pad carrier and the magnetic body, wherein spring elements supported on the magnetic body press on the armature disk, in particular such that when the ring winding is energized, the armature disk is pulled towards the magnetic body and when the armature disk is not energized, the armature disk presses the brake pad carrier onto a braking surface formed on a part connected to the second housing, in particular a flat and finely machined surface.

7. Geared motor according to one of the preceding claims, characterized in that a torque support, in particular a disc-like one, is detachably and / or rotationally fixed connected to the first housing, in particular wherein spacer bolts are arranged between the torque support and the first housing, in particular wherein the central axes of the spacer bolts lie in a plane whose normal is directed perpendicular to the axis of rotation of the rotor shaft of the electric motor, in particular wherein the number of spacer bolts is two, wherein the second housing is detachably and / or rotationally fixed connected to the torque support.

8. Geared motor according to one of the preceding claims, characterized in that the spacer bolts are designed as hollow cylinders, in particular wherein the spacer bolts are made of plastic, wherein first screws protrude through the spacer bolts, through the torque support and through the second housing and are screwed with their respective threaded area into a respective axial bore of the first housing, in particular of the cover part, wherein the respective screw head of the respective first screw presses the second housing towards the torque support, in particular and thus the spacer bolts are pressed towards the first housing.

9. Geared motor according to one of claims 1 to 6, characterized in that the spacer bolts are designed as hollow cylinders, wherein first screws project through the spacer bolts and through the torque arm and are screwed with their respective threaded portion into a respective axial bore of the first housing, in particular the cover part, wherein the respective screw head of the respective first screw presses the torque arm towards the spacer bolts, in particular the spacer bolts are thus pressed towards the first housing, in particular wherein the second housing is pressed against the torque arm by means of second screws, wherein the second screws with their threaded portion in Threaded holes of the torque support are screwed in.

10. Geared motor according to one of the preceding claims, characterized in that the torque support is designed eccentrically, in particular such that the radial distance to the axis of rotation of the intermediate shaft is variable as a function of the circumferential angle, in particular with respect to this axis of rotation, and / or has different values.

11. Geared motor according to one of the preceding claims, characterized in that the torque support is attached to the first housing, in particular to the cover part of the first housing, by means of the first screws, wherein at least two first screws have a smaller radial distance to the axis of rotation of the intermediate shaft than a third of the first screws.

12. Geared motor according to one of the preceding claims, characterized in that a first bearing, in particular a rolling bearing, is provided in the cover part for rotatable mounting of the intermediate shaft, wherein a second bearing, in particular a rolling bearing, is provided in the lower part for rotatable mounting of the intermediate shaft.

13. Geared motor according to one of the preceding claims, characterized in that a first and a second bearing are arranged in the gearbox for rotatable mounting of the intermediate shaft, wherein an inner ring of the first bearing is mounted on the intermediate shaft and an outer ring of the first bearing is received in the cover part, wherein an inner ring of the second bearing is mounted on the intermediate shaft and an outer ring of the second bearing is received in the lower part.

14. Geared motor according to one of the preceding claims, characterized in that the torque support is shaped eccentrically and / or the first, in particular at least one, screw which has the largest radial distance to the axis of rotation of the intermediate shaft has a smaller radial distance to the axis of rotation of the driving shaft than to the axis of rotation of the intermediate shaft.

15. Geared motor according to one of the preceding claims, characterized in that the driving shaft is aligned parallel to the intermediate shaft.

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