DE102012008652A1 - Gear motor, has rotor shaft supported in motor housing by fixed motor bearing, and driving shaft put into receiving bore of rotor shaft such that driving shaft is actuated and positively connected with rotor shaft in torque-proof manner - Google Patents

Abstract

The motor has a gearbox (23) drivable by a motor (24) that comprises a motor housing (12) and a rotor shaft (11), where the rotor shaft is supported in the motor housing by fixed motor bearings (10). The gearbox comprises a gear housing (15), bearings (3, 5) and a driving shaft (1) that is supported in the gear housing by the bearings. The driving shaft is put into a receiving bore (8) of the rotor shaft such that the driving shaft is actuated and positively connected with the rotor shaft in a torque-proof manner. The driving shaft comprises a gearing (22). The gearbox is designed as a two-stage spur gear. An independent claim is also included for a shaft for fastening in a receiving bore of a rotor shaft.

Description

The invention relates to a geared motor and a shaft.

From the DE10137024B4 are known a series of shafts and a method for manufacturing, wherein the shaft attachment is produced inexpensively and with little effort by the shaft is inserted into a receiving part. The disadvantage here is the susceptibility of the shaft attachment against transverse forces, whereby the scope is reduced to planetary gear.

The invention is therefore the object of developing a geared motor and a shaft, the reliability is increased.

According to the invention the object is achieved in the geared motor according to the features indicated in claim 1 and in the shaft according to the features indicated in claim 15.

Important features of the invention in the geared motor are that the geared motor has an engine and a gear that can be driven by the engine,
the motor having a motor housing and a rotor shaft mounted in the motor housing by means of at least two motor bearings,
wherein the transmission comprises a transmission housing, at least one bearing and a driving shaft, wherein the driving shaft of the transmission is mounted by means of the bearing in the transmission housing,
wherein the driving shaft of the transmission is inserted in a receiving bore of the rotor shaft,
in particular, wherein the driving shaft rotatably, in particular non-positively and positively, is connected to the rotor shaft.

The advantage here is that the transmission can be connected in a simple manner with the engine, since no additional coupling between the rotor shaft of the motor and the driving shaft of the transmission is required. The additional storage of the driving shaft is an additional heat conduction, whereby heat from the rotating part to the transmission housing can be dissipated, and thus allows the transmission housing heat dissipation of the driving shaft and with this positively connected rotor shaft to the gear housing out. Thus, the risk of temperature damage, for example, on a toothing, reducible and improves the reliability of the geared motor.

Since the additional bearing with a small radial extent is executable, the heat generated by the camp itself is low.

Furthermore, by means of the bearing of the driving shaft, transverse forces, which are exerted on the driving shaft, can be compensated, so that the transmission can be used for higher torques. Thus, the smoothness of the driving shaft is also improved, because a radial deflection of the shaft can be prevented. As a result, the wear on the toothing parts of the transmission can be reduced, thus improving the service life and the reliability of the geared motor.

In an advantageous embodiment, the driving shaft has a toothing, in particular wherein the shaft has a toothed portion, in particular a toothed portion integrally formed with the shaft. The advantage here is that the shaft can be brought directly into engagement with a further toothing part and as connecting means such as couplings can be saved.

In an advantageous embodiment, the bearing is arranged on the side facing away from the engine of the toothing, in particular wherein the bearing, in particular the inner ring of the bearing, is arranged on an axial region of the driving shaft such that arranged between this axial region and the engine, the toothing is. The advantage here is that the driving shaft in the radial direction is only slightly deflected, with transverse forces are absorbed by the camp.

In an advantageous embodiment, the diameter of the outer ring of the bearing is smaller than the diameter of the inner ring of the engine mount or the inner rings of the engine mounts of the rotor shaft in the motor housing. The advantage here is that the rotational speed of the driving shaft in the bearing is smaller than the rotational speed of the rotor shaft in the or the engine mounts. As a result, the friction in the bearing is smaller and less heat is generated. Thus, a heat dissipation of the driving shaft and the rotor shaft connected thereto is made possible by the bearing and only a small additional heat flow is generated by the bearing itself.

In an advantageous embodiment, the bearing and / or motor bearing is composed of metallic parts and / or designed as a rolling bearing, in particular designed as a ball roller bearing. The advantage here is that these bearings have essentially rolling friction and the rolling friction is very low. Thus, the friction and the associated heat development are reduced.

In an advantageous embodiment, the driving shaft is electrically conductive via the bearing and thus also thermally conductively connected to the transmission housing. The advantage here is that heat generated at the driving shaft on the Bearing is derivable to the transmission. Thus, the bearing is part of the associated heat path.

In an advantageous Absgestaltung the bearing is designed as a floating bearing. The advantage here is that the axial position of the driving-in time is variable, so that temperature-induced deformations of the components in the axial direction are compensated, in particular, thermal expansion can be compensated.

In an advantageous embodiment, an engine mount is designed as a fixed bearing. The advantage here is that axial forces acting on the rotor shaft and the driving-in time by means of this fixed bearing can be accommodated. Thus, the connection of the driving shaft is relieved with the rotor shaft and the bearing of the driving shaft is significantly smaller executable than the engine mounts. Thus, the heat generation at the bearing of the driving-in time is reducible and heat of the driving shaft and the rotor shaft can be dissipated by means of the connection of the shaft with the bearing and thus with the transmission housing.

In an alternative embodiment, the bearing are designed as a fixed bearing and the motor bearings as floating bearings, in particular wherein the bearing has a larger outer ring than the outer rings of the engine mounts. The advantage here is that the heat generated during operation in the warehouse via the gear housing part can be derived from the environment. In this way, a lower heat is also generated in the designed as floating bearings engine mounts, especially when high axial forces. In development is even between the gear housing and the motor housing a heat barrier einbring bar, so that the heat of the bearing can only be dissipated via the transmission housing. In this way, moreover, the engine and its engine mounts are very compactly executable.

In an advantageous embodiment, a further toothing part with a further, mounted in the transmission housing via further bearing shaft, in particular intermediate shaft or aborting shaft, the transmission rotatably connected,
wherein the further toothing part is engaged and / or meshes with the toothing of the driving shaft,
wherein the toothing with the further toothing part forms a straight-toothed spur gear stage or helical spur gear stage or an angular gear stage, in particular a bevel gear stage. The advantage here is that the driving shaft according to the invention is suitable for a variety of transmission types, so that a modular system of transmissions is made possible with a reduced number of parts. As a result, the storage costs can be reduced and the environment is protected.

In an advantageous embodiment, a bearing of a driven shaft of the transmission is received in a web, in which also the bearing of the driving shaft is received,
wherein the land extends inwardly from the outer wall of a transmission housing portion of the transmission housing. The advantage here is that the transmission is compact. In this case, a good heat dissipation of the driving shaft is possible because in a transmission with translation into the slow the driven shaft rotates slowly and thus little heat is generated at the bearing of the driven shaft. Thus, a heat dissipation from the bearing of the driving shaft to the outer wall of the transmission housing is made possible.

In an advantageous embodiment, the web has a smaller extent in the axial direction than in the radial direction. The advantage here is that the transmission is compact. Due to the narrow design of the web, this has a large surface, which is cooled by means of the transmission oil.

In an advantageous embodiment, the web is made in one piece with the gear housing part. The advantage here is that the heat dissipation of the web to the outer wall takes place directly in the one-piece housing part. Additional heat transfer can be saved.

In an advantageous embodiment, a gear member rotatably connected to the output shaft has a larger outer diameter than the outer diameter of the disposed in the web outer ring of the bearing of the driven shaft,
in particular, wherein the toothed part rotatably connected to the driven shaft is arranged on the side of the bearing of the driven shaft facing away from the motor. The advantage here is that the toothing allows a large translation of the transmission.

In an advantageous embodiment, the axial area of the gear covered by the web is spaced from the axial area of the gear covered by the toothing of the driving shaft. The advantage here is that the teeth of the driving shaft is spaced from the web. Thus, a collision of the teeth can be prevented with the bridge and increases the reliability.

In an advantageous embodiment, all bearings of the transmission are arranged in a one-piece gear housing part. The advantage here is that a uniform cooling of all bearings of the transmission is possible.

In an advantageous embodiment, the further toothing part is made of plastic, in particular wherein the further toothing part is made of thermoplastic, preferably polyamide. The advantage here is that plastic can be manufactured in a simple manner, for example, the toothed part as Kunststoffgussteil be manufactured. The plastic is softer and more elastic than steel, so the friction is very small. Thus, no lubricating oil in the transmission is necessary and the noise emissions are lower.

In an advantageous embodiment, the transmission is executed lubricating oil-free, the bearings may have fat. The advantage here is that the transmission is inexpensive to manufacture. In addition, the environment is protected, since no waste oil must be disposed of and no oil escapes from the transmission.

In an advantageous embodiment, the driving shaft of the transmission is made of tempered steel and / or surface hardened steel. The advantage here is that steel has a low thermal expansion and at the same time a good thermal conductivity. In addition, steel is easy to process and inexpensive.

In an advantageous embodiment, the gear housing part is produced as a cast part, in particular wherein the gear housing part is manufactured as a cast steel part, cast iron part and / or cast aluminum part. The advantage here is that the gear housing part can be manufactured as a cast part in a simple manner, in particular, the complex geometry of the gear housing part is in one step finished in a few steps.

In an advantageous embodiment, the toothing part of the aborting shaft is made of case hardened steel. The advantage here is that case steel is a standard material that can be processed in a simple manner.

In an advantageous embodiment, the driving shaft has a nanocrystalline surface,
wherein the grain size is less than 100 nm, preferably less than 30 nm. The advantage here is that nanocrystalline material is characterized by particular mechanical properties. It is significantly harder and more wear resistant compared to the same coarse microstructure material. The sliding properties are also very good, so that the friction in the bearing can be reduced and thus the development of heat can be reduced.

In an advantageous embodiment, the driving shaft has a nanocrystalline coating. The advantage here is that the coating can be applied after shaping of the shaft and the material of the coating is independent of the material of the shaft selectable.

In an advantageous embodiment, the coating is carbonaceous and / or containing silicon. The advantage here is that these nanocrystalline coatings are particularly hard and have a high grain size stability.

In an advantageous embodiment, the layer thickness of the coating is less than a micrometer,
in particular wherein the layer thickness is less than 200 nm and greater than 50 nm. The advantage here is that the cost of materials for the coating is low and good adhesion of the layer is possible.

Important features of the invention in the shaft for mounting in a receiving bore of a rotor shaft, wherein the rotor shaft of a motor, in particular electric motor, is included, wherein the shaft is a driving shaft for a transmission are that
the shaft has at least nine axial shaft sections A, B, C, D, E, F, G, H, I adjacent to one another in alphabetical order of the letters designating them and of which F has a larger maximum outer diameter than A, B, C, D, E, G, H and / or I,
wherein the shaft portion D is toothed and / or knurled,
wherein the shaft portion F has a helical or spur toothing,
wherein the shaft portion H is cylindrical.

The advantage here is that the shaft is inserted as an input shaft of the transmission in the rotor shaft. The shaft section D connects the receiving bore with the shaft by cutting the knurling and / or the toothing into the receiving bore. The driving shaft meshes by means of the toothing of the shaft section F with a further toothing part of the transmission. Thus, the driving shaft also acts as a kind of clutch and as driving gearing. So it is the number of components reduced. Thus, the environment is protected. At the same time the connection is particularly secure by a connectable to the shaft portion H bearing, which is arranged in the housing interior.

In an advantageous embodiment of the shaft portion G is made chamfered in the axial direction and the shaft diameter decreases from the shaft portion F to the shaft portion H down. The advantage here is that the shaft portion G limits the shaft portion H in the axial direction to the shaft portion F, so that the connectable to the shaft portion H bearing does not collide with the toothing of the shaft portion G.

In an advantageous embodiment of the shaft portion I is made chamfered in the axial direction and the shaft diameter decreases from the shaft portion H to the transmission side shaft end down. The advantage here is that the shaft section I acts as Einfädelhilfe for the shaft in the camp.

In an advantageous embodiment, the shaft is arranged in a gear motor with the properties described above. The advantage here is that by means of the shaft a simple and cost-effective connection of the transmission with the engine is made possible, which is particularly safe executable.

Further advantages emerge from the subclaims. The invention is not limited to the combination of features of the claims. For the skilled person, further meaningful combination options of claims and / or individual claim features and / or features of the description and / or figures, in particular from the task and / or the task posing by comparison with the prior art arise.

The invention will now be explained in more detail with reference to figures:

In the 1 an inventive geared motor is drawn in sectional view.

In the 2 a geared motor according to the invention is shown in plan view.

3 shows a shaft according to the invention in plan view.

The in 1 and 2 shown geared motor has a gearbox 23 and a motor 24 on. The gear 23 is designed as an at least two-stage spur gear. It has an abortive wave 1 on, which by means of a first camp 3 and a second camp 5 in a gear housing part 15 is stored.

The wave 1 is with a toothing part, in particular gear 4 , which is connected with a toothing section 22 another wave 20 engaged. The further wave 20 is with a further toothing part, in particular gear 18 , which is connected to a toothed portion of a driving shaft, in particular pinion shaft 7 engaged. The further wave 20 is by means of two bearings 19 and 25 in the gearbox part 15 stored.

The pinion shaft 7 is by means of a warehouse 6 in the transmission housing part 15 stored. This is the camp 6 on the side facing away from the engine of the toothed portion of the pinion shaft 7 arranged.

The warehouse 6 is preferably designed as a floating bearing. A floating bearing is a bearing that allows not only the rotational movement of the shaft, at least in a limited Beriech a displacement of the shaft in the axial direction.

The shaft axis direction of the pinion shaft 7 is defined as the axial direction. The radius of the pinion shaft 7 defines the radial direction.

The warehouse 6 is designed as a bearing receiving part 27 in which a rolling bearing is added. The bearing receiving part 27 is metallic, preferably made of steel, in particular made of free-cutting steel. The bearing receiving part 27 is manufactured by means of a turning process. Here is the bearing receiving part 27 pressed into the gear housing part 15 , Preferably, between the bearing receiving part 27 and the transmission housing part 15 Thermal paste arranged.

Thus, all the shafts of the transmission 23 in the integrally running gear housing part 15 stored.

The transmission housing part 15 has a web which integrally with the gear housing part 15 is executed. The bridge is located inside the gear housing part 15 arranged. The web thus extends from the outer wall of the gear housing part 15 of the gearbox housing inside. In this case, the web has a smaller extent in the axial direction than in the radial direction. In particular, the axial area of the gear covered by the web is 23 spaced from the axial region of the transmission covered by the toothing of the driving shaft 23 ,

In the dock are the camp 5 the abortive wave 1 of the transmission 23 and the camp 6 the pinion shaft 7 added. This shows that with the aborting wave 1 non-rotatably connected gear 4 a larger outer diameter than the outer ring of the arranged in the web bearing 5 the abortive wave 1 , That with the abortive wave 1 non-rotatably connected gear 4 is on the engine 24 opposite side of the camp 5 the abortive wave 1 arranged.

The warehouse 5 the abortive wave 1 is by means of a locking ring 28 in the web of the gear housing part 15 fixed. Here is the circlip 28 in the axial direction between the bearing 5 the driven shaft and the bearing receiving part 27 arranged. Preferably, the locking ring 28 with the warehouse 5 and the transmission housing part 15 releasably positively connected.

The outer diameter of the circlip 28 is smaller than the outer diameter of the bearing receiving part 27 , Thus, the circlip 28 insertable into a recess in the transmission housing part 15 into which the bearing receiving part can be pressed.

The pinion shaft 7 is designed as a Einsteckritzel. It is with a receiving hole 8th in a rotor shaft 11 of the motor 24 rotatably, in particular positively and positively connected. The rotor shaft 11 is by means of a first engine mount 10 and a second engine mount, not shown stored. This is the first engine mount 10 the rotor shaft 11 in a bearing flange 13 arranged and the second motor bearing of the rotor shaft is in a motor housing 12 arranged. One of the motor bearings of the rotor shaft is designed as a fixed bearing.

A bearing is in this case a bearing which allows the mounted shaft a rotational movement and fixes the shaft in the axial direction and against the axial direction. Thus, even with thermally induced expansions of the shaft no axial displacement of the bearing is possible.

Such bearings are particularly advantageous in combination with floating bearings, as at a thermal load of the shaft, this expands and the change in length in the axial direction by means of the movable bearing is compensated, while the fixed bearing clearly defines the axial position of at least a portion of the shaft.

Here are the abortive wave 1 , the further wave 20 , the pinion shaft 7 and / or the rotor shaft 11 at least coaxially arranged. Camps ( 3 . 5 . 6 . 25 ) and the engine mounts 10 are designed as rolling bearings, in particular designed as ball bearing. Preferably, the parts of the bearings ( 3 . 5 . 6 . 25 ) and the engine mount 10 metallic, in particular, the inner ring, the outer ring and the rolling elements are metallic. Thus, the inner ring is electrically conductive and therefore also thermally conductively connected to the outer ring. One in one of the camps ( 3 . 5 . 6 . 25 ) mounted shaft is thus by means of the camp ( 3 . 5 . 6 . 25 ) thermally conductively connected to the transmission housing part 15 , The electrical connection also allows for easy grounding of the rotor of the motor by means of a ground connection of the gear housing.

The warehouse 6 the pinion shaft 7 has an outer ring. The engine mounts each have an inner ring. Here is the diameter of the outer ring of the bearing 6 the pinion shaft smaller than the diameter of the inner ring of the engine mounts or the engine mount 10 ,

The bearing flange 13 has a sealing plug 9 on, which allows a pressure equalization of the interior of the transmission housing with the environment. In Rotorwellenachsrichtung is the gearbox side of the engine mount 10 a shaft seal 17 in the bearing flange 13 arranged.

The bearing flange 13 is positively by means of a fastener 14 with the gear housing part 15 connected. Preferably, the bearing flange 13 with the gear housing part 15 bolted, with the fastener 14 designed as a connecting screw.

At the bearing flange 13 a centering collar is incorporated, so that a centering of the gear housing part 15 on the bearing flange 13 is made possible in a simple manner.

On the output side is the gear housing part 15 by means of a mounting flange 2 positively connected with an application, not shown. Another gearbox part 26 is designed as a cover of the gear housing: This further gear housing part 26 closes a mounting hole in the gear housing part 15 , When mounting the gearbox 23 the gears ( 4 . 18 ) through the mounting opening into the gear housing part 15 brought in.

The transmission housing thus comprises at least the transmission housing parts 15 and 26 , The gearbox parts 15 and 26 are preferably designed as castings, for example, designed as steel castings, cast iron parts or aluminum castings. The pinion shaft 7 is made of tempered steel and / or surface hardened steel.

In the 3 illustrated pinion shaft 7 has nine axial shaft sections (A, B, C, D, E, F, G, H, I). In this case, the shaft portion A at the rotor shaft side end of the pinion shaft 7 arranged. The shaft section A is bevelled and acts as a centering aid for the threading of the pinion shaft 7 into the receiving hole 8th , The shaft portion B adjacent to the shaft portion A is cylindrical and preferably has a spiral groove 30 for venting. The spiral groove 30 is one on the circumference of the pinion shaft 7 along screwing groove.

The shaft portion C is attached to the shaft portion B and provides a chip space for insertion of the pinion shaft 7 into the receiving hole 8th accumulating chips ready. The shaft section C is executed as an undercut.

The shaft section C is adjoined by the shaft section D, which is provided with knurling. The knurling is used to cut the pinion shaft 7 into the receiving hole 8th during the Insertion. Here is the largest outer diameter of the pinion shaft 7 in the region D larger than the mean inner diameter of the receiving bore 8th ,

The shaft portion E connects the shaft portion D with the shaft portion F. In this case, the shaft portion E is made chamfered in the axial direction, in particular, the diameter of the shaft portion E increases in the axial direction from D to F. The shaft section F has a toothing, which in the installed state in the transmission 23 with the gear 18 engaged. The toothing is preferably designed as helical or straight toothing. In particular, during the production of the toothing of the shaft section F also in the knurling of the shaft section D is cut, if the largest outer diameter of the shaft section D is greater than the root diameter of the toothing of the shaft section F.

The largest outer diameter of the shaft section F is greater than the largest outer diameter of the shaft sections A, B, C, D, E, G, H and / or I.

The shaft portion G acts as a transition from the toothed shaft portion F to the cylindrical shaft portion H. In this case, the shaft portion G is made chamfered in the axial direction and its diameter decreases from F to H. The shaft section H is form-fitting with an inner ring of the bearing 6 connectable.

Between the rotor shaft 11 remote end of the pinion shaft 7 and the shaft portion H, the shaft portion I is arranged. The shaft portion I is made chamfered in the axial direction, its diameter increases towards the shaft portion H to. Thus, the shaft portion I acts as a threading aid for the pinion shaft 7 in the warehouse 6 ,

In further embodiments of the invention, the further toothing part, in particular gear 18 , which with the pinion shaft 7 engaged, made of plastic. Preferably, the gear is 18 a plastic casting, which is made of thermoplastic, preferably polyamide, in particular the material PA46.

Plastic is much softer than the steel that makes up the pinion shaft 7 is made, so the friction is very small and additional lubrication is unnecessary. The gear 23 is thus oil-free executable, the bearings can be performed greased.

The warehouse 6 dissipates the heat of the driving gearing to the gear housing. Thus, the resulting heat upon engagement of the plastic gear with the driving toothing heat is dissipated via the metallic running driving gearing and from there at least partially over the bearing 6 and the gearbox housing to the environment.

In further embodiments of the invention, the transmission is designed as an angle gear, preferably, the transmission is designed as a bevel gear. This is the pinion shaft 7 designed as bevel pinion and helical toothed. The shaft portion F is made substantially conically shaped, in particular, the shaft portion F is designed as a truncated cone, wherein the base diameter of the shaft portion F to the shaft portion G decreases.

The bevel of the shaft section E is designed significantly steeper in a bevel gear as in a spur gear. The angle between the lateral surface of the shaft section E and the rotor shaft axis is between 70 ° and 90 °, preferably between 80 ° and 90 °.

In further embodiments of the invention, the pinion shaft 7 made of case-hardened steel and has a nanocrystalline coating. Preferably, this coating contains carbon and / or silicon. The thickness of the coating is less than one micron, in particular less than 200 nm and greater than 50 nm. As coating methods, physical gas phase deposition methods and / or chemical vapor deposition methods are used. The crystalline grain size of the coating is less than 100 nm, in particular, the grain size is smaller than 30 nm. Preferably, metals and metallic alloys are used as the nanocrystalline material. Nanocrystalline coatings are characterized by high hardness, low sliding friction losses and good wear properties, with low material costs. Thus, the heat development is reduced by friction on the camp.

In further embodiments of the invention are the driving shaft and the driven shaft of the transmission 23 coaxially aligned and arranged.

LIST OF REFERENCE NUMBERS

1

wave

2

mounting flange

3

camp

4

gear

5

camp

6

camp

7

pinion shaft

8th

location hole

9

sealing plug

10

motor bearings

11

rotor shaft

12

motor housing

13

Lagerflansch

14

Fastening means, in particular connecting screw

15

Gear housing part

17

Shaft seal

18

gear

19

camp

20

wave

21

Shaft seal

22

toothed section

23

transmission

24

engine

25

camp

26

Gear housing part

27

Bearing receiving part

28

circlip

30

spiral

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 10137024 B4 [0002]

Claims (15)

A geared motor comprising an engine and a transmission drivable by the engine, the engine having a motor housing and a rotor shaft supported by at least two engine mounts in the engine housing, the transmission having a transmission housing, at least one bearing and a driving shaft, wherein also, the input shaft of the transmission is mounted in the transmission housing by the bearing, characterized in that the input drive shaft of the transmission is inserted into a receiving bore of the rotor shaft, in particular wherein the input drive shaft in a rotationally fixed, in particular non-positively and positively, is connected to the rotor shaft. Geared motor according to at least one of the preceding claims, characterized in that the driving shaft has a toothing, in particular wherein the shaft has a toothed section, in particular a toothed section formed in one piece with the shaft. Geared motor according to at least one of the preceding claims, characterized in that the bearing is arranged on the side of the toothing remote from the motor, in particular wherein the bearing, in particular the inner ring of the bearing, is arranged on an axial region of the driving shaft such that the toothing is arranged between this axial region and the motor. Geared motor according to at least one of the preceding claims, characterized in that the diameter of the outer ring of the bearing is smaller than the diameter of the inner ring of the engine mount or the inner rings of the engine mounts of the rotor shaft in the motor housing. Geared motor according to at least one of the preceding claims, characterized in that the bearing and / or motor bearing is composed of metallic parts and / or designed as rolling bearings, in particular designed as ball roller bearings, in particular wherein the driving shaft is electrically conductively connected via the bearing and thus also thermally conductively connected to the transmission housing. Geared motor according to at least one of the preceding claims, characterized in that the bearing is designed as a floating bearing and a motor bearing as a fixed bearing or that the bearing is designed as a fixed bearing and the motor bearings as a floating bearing, in particular wherein the bearing has a larger outer ring than the outer rings of the engine mounts and / or wherein a thermal barrier between the gear housing and the motor housing is arranged. Geared motor according to at least one of the preceding claims, characterized in that a further toothing part is rotatably connected to a further shaft mounted in the gearbox housing via further bearings, in particular intermediate shaft or aborting shaft, of the gearbox, wherein the further toothing part is engaged and / or meshes with the toothing of the driving shaft, wherein the toothing with the further toothing part forms a straight-toothed spur gear stage or helical spur gear stage or an angular gear stage, in particular a bevel gear stage. Geared motor according to at least one of the preceding claims, characterized in that a bearing of a driven shaft of the gear is received in a web, in which also the bearing of the driving shaft is received, wherein the bridge extends inwardly from the outer wall of a transmission housing part of the transmission housing, in particular wherein the web has a smaller extent in the axial direction than in the radial direction, in particular wherein the web is made in one piece with the gear housing part. Geared motor according to at least one of the preceding claims, characterized in that a toothed part connected in a rotationally fixed manner to the aborting shaft has a larger outer diameter than the outer diameter of the outer ring of the abutment shaft bearing arranged in the web; wherein the gear rotatably connected to the driven shaft gear member is disposed on the side facing away from the engine of the bearing of the driven shaft. and / or that the axial region of the gear covered by the web is spaced from the axial region of the gear covered by the toothing of the driving shaft. Geared motor according to at least one of the preceding claims, characterized that all bearings of the transmission are arranged in a one-piece gearbox housing part. Geared motor according to at least one of the preceding claims, characterized in that the further toothing part is made of plastic, in particular wherein the further toothing part is made of thermoplastic, in particular polyamide. Geared motor according to at least one of the preceding claims, characterized in that the transmission is designed oil-free. Geared motor according to at least one of the preceding claims, characterized in that the driving shaft of the gearbox is made of tempered steel and / or surface hardened steel and / or that the gear housing part is made as a casting, in particular wherein the housing part is manufactured as a cast steel part, cast iron part and / or cast aluminum part. and / or that the toothing part of the further shaft and / or the toothing part of the aborting shaft are made of case-hardened steel. Geared motor according to at least one of the preceding claims, characterized in that the driving shaft has a nanocrystalline surface, wherein the grain size is less than 100 nm, preferably less than 30 nm, in particular, wherein the driving shaft has a nanocrystalline coating, in particular wherein the coating is carbonaceous and / or contains silicon, in particular, wherein the layer thickness of the coating is less than a micrometer, in particular wherein the layer thickness is less than 200 nm and greater than 50 nm. Shaft for mounting in a receiving bore of a rotor shaft, wherein the rotor shaft is comprised by a motor, in particular an electric motor, wherein the shaft is a driving shaft for a transmission, characterized in that the shaft has at least nine axial shaft sections A, B, C, D, E, F, G, H, I adjacent to one another in alphabetical order of the letters designating them and of which F has a larger maximum outer diameter than A, B, C, D, E, G, H and / or I, wherein the shaft portion D is toothed and / or knurled, wherein the shaft portion F has a helical or spur toothing, wherein the shaft portion H is cylindrical, in particular, wherein the shaft portion G is made slanted in the axial direction and the shaft diameter decreases from the shaft portion F to the shaft portion H, in particular, wherein the shaft portion I is made slanted in the axial direction and the shaft diameter decreases from the shaft portion H to the transmission-side shaft end, in particular wherein the shaft is arranged in a geared motor according to at least one of the preceding claims.

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