DE102020002698A1 - Transmission with a gear having a toothing and pinions each having a pinion toothing - Google Patents

Abstract

Transmission with a wheel having a toothing and pinion gears each having a pinion toothing, in particular wherein the wheel is mounted rotatably about an axis of rotation and / or the pinions are mounted rotatably about a respective axis of rotation, the pinion teeth being in engagement with the toothing and / or mesh, wherein the respective axis of rotation of the pinion, in particular pinion teeth, is each aligned skew to the axis of rotation of the wheel.

Description

The invention relates to a transmission with a gear having a toothing and pinions each having a pinion toothing.

From the US 2011/0209573 A1 a transmission is known.

A transmission with a toothed part is known from US 2009/038 435 A1.

From the DE 202 12 935 U1 a linear drive for adjusting movably mounted parts is known.

From the DE 10 2017 000 304 B3 a drive with a summing gear driven by electric motors is known.

From the DE 10 2016 118 877 A1 a mechanical transmission arrangement is known.

The invention is therefore based on the object of developing a transmission in a compact and efficient manner.

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

Important features of the invention in the transmission with a gear having a toothing and pinion gears each having a pinion toothing are that the wheel is rotatably mounted about an axis of rotation and / or the pinions are rotatably mounted about a respective axis of rotation,
wherein the pinion teeth are each in engagement with the teeth and / or mesh,
wherein the respective axis of rotation of the pinion, in particular pinion toothing, is aligned skew to the axis of rotation of the wheel.

The advantage here is that the transmission can be made very compact and a high degree of efficiency can be provided.

In an advantageous embodiment, the pinion teeth are unevenly spaced from one another in the circumferential direction with respect to the axis of rotation of the wheel. The advantage here is that the running smoothness is improved and the noise emission is reduced.

In an advantageous embodiment, the pinion gears are evenly spaced from one another in the circumferential direction in relation to the axis of rotation of the wheel. The advantage here is that a holding part for receiving the driving electric motors can be designed with a discrete symmetry and thus can also be assembled in several parts from structurally identical parts.

In an advantageous embodiment, the wheel is a spur gear, in particular the toothing being a spur gear. The advantage here is that the spur gear can be designed as a conical wheel, that is to say as a conical wheel which is toothed on its radial outer side.

In an advantageous embodiment, the envelope of the toothing of the wheel is a truncated cone,
In particular, the rotational body determined by the maximum radial distance with respect to the rotational axis of the wheel is a truncated cone, the rotational symmetry axis of the rotational body being the rotational axis of the wheel. Is beneficial
in the process, that a high degree of efficiency can be provided with a high gear ratio and a high maximum torque that can be transmitted.

In an advantageous embodiment, the envelope of the pinion toothing is a truncated cone,
in particular wherein the rotational body determined by the maximum radial distance with respect to the axis of rotation of the pinion toothing is a truncated cone, the rotational symmetry axis of the rotational body being the rotational axis of the pinion toothing. The advantage here is that a high degree of efficiency can be provided with a high gear ratio and a high maximum torque that can be transmitted.

In an advantageous embodiment, the angle between the axis of rotation of the pinion toothing and the axis of rotation of the wheel is between 10 ° and 13 °. The advantage here is that only small losses occur.

In an advantageous embodiment, the cone angle of the truncated cone of the wheel differs from the cone angle of the truncated cone of the pinion toothing. The advantage here is that only small losses occur.

In an advantageous embodiment, the toothing of the wheel has a first helix angle, i.e. is helical,
wherein the pinion toothing has a second helix angle, that is to say is helically toothed, the second helix angle being greater than the first helix angle,
in particular where the first helix angle differs from the second helix angle by 1.5 ° to 6 °, in particular by 3 °,
in particular where the first helix angle is between 25 ° and 60 °, in particular where the total overlap exceeds the value 2.5. The advantage here is that a high degree of efficiency, low losses can be achieved and a high torque can be achieved in a small installation space.

In an advantageous embodiment, the wheel is designed to be narrower than the respective pinion, in particular than the respective pinion toothing. The advantage here is that a high overlap can be achieved even with a narrow wheel.

In an advantageous embodiment, the wheel and the pinion are made of case-hardened steel. The advantage here is that inexpensive, simple production is possible. In addition, phosphating can also be carried out. This then causes an improved running-in of the toothing.

In an advantageous embodiment, the pinion teeth are driven by electric motors and mesh with the teeth of the wheel,
wherein the pinions are made identical to one another, in particular all are made identical to one another. The advantage here is that the gear can be manufactured as a summing gear without any special effort.

• - dass die Rotorwelle des jeweiligen Elektromotors einen nicht verschwindenden Winkel zu der Normalen der Ebene aufweist
• - und/oder dass eine Berührfläche zwischen dem jeweiligen Lagerflansch und einem Gehäuseteil des jeweiligen Elektromotors eben ausgeführt ist und einen nicht verschwindenden Winkel zu der Ebene aufweist.

In an advantageous embodiment, the transmission has a holding part which is connected to a housing part of the transmission,
wherein a shaft of the transmission, in particular the output shaft of the transmission, connected to the wheel in a rotationally fixed manner, is rotatably mounted by means of a bearing which is received in the holding part or housing part,
each pinion being non-rotatably connected to a rotor shaft of a respective electric motor, which is rotatably mounted relative to a bearing flange of the respective electric motor,
in particular where the respective bearing flange receives a respective bearing of the respective rotor shaft,
in particular wherein the respective bearing flange is made in one piece, in particular in one piece,
each bearing flange is connected to the holding part,
wherein the contact surfaces between the holding part and the bearing flanges are flat and are arranged in a common plane,
each bearing flange is shaped like a wedge,

• - That the rotor shaft of the respective electric motor has a non-vanishing angle to the normal of the plane
• and / or that a contact surface between the respective bearing flange and a housing part of the respective electric motor is designed to be flat and has a non-vanishing angle to the plane.

The advantage here is that as a result of the wedge-shaped design of the bearing flanges, the holding part has a shape that is easy to manufacture. The bearing flanges of the electric motors are designed to be wedge-shaped in an unusual way, but they can all be constructed identically to one another. This means that only one and the same type of bearing flange has to be produced. The effort involved in producing such wedge-shaped bearing flanges with a high degree of accuracy is therefore sensible. Wedge-shaped here means that the wall thickness of the bearing flange in a direction perpendicular to the axis of rotation of the rotor shaft of the corresponding electric motor is a monotonically increasing, in particular strictly monotonically increasing, function.

In an advantageous embodiment, the holding part is made in one piece, in particular in one piece. The advantage here is that the relative alignment of the electric motors to one another can be fixed by means of the holding part.

In an alternative advantageous embodiment, the transmission has a holding part which is connected to a housing part of the transmission,
wherein a shaft of the transmission, in particular the output shaft of the transmission, connected to the wheel in a rotationally fixed manner, is rotatably mounted by means of a bearing which is received in the holding part or housing part,
each pinion being non-rotatably connected to a rotor shaft of a respective electric motor, which is rotatably mounted relative to a bearing flange of the respective electric motor,
wherein the holding part is designed in several parts, in particular in several parts, i.e. has parts connected to one another,
wherein the parts are structurally identical to one another, in particular therefore identical
each part being connected to only a single respective bearing flange and a respective contact surface between the respective part and the respective bearing flange being encompassed by a plane whose normal is aligned parallel to the axis of rotation of the rotor shaft of the electric motor belonging to the respective bearing flange. The advantage here is that the structurally identical parts of the holding part can always be manufactured in the same way and then only have to be connected particularly precisely.

Further advantages result from the subclaims. The invention is not restricted to the combination of features of the claims. For the person skilled in the art, there are further meaningful possible combinations of claims and / or individual claim features and / or features of the description and / or the figures, in particular from the task and / or the task presented by comparison with the prior art.

• In der 1 sind die Verzahnungsteile eines erfindungsgemäßen Getriebes in Schrägansicht dargestellt.
• In der 2 ist das Getriebe in Schrägansicht dargestellt.

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

• In the 1 the toothing parts of a transmission according to the invention are shown in an oblique view.
• In the 2 the transmission is shown in an oblique view.

As shown in the figures, the transmission has an externally toothed, in particular face-toothed, wheel 2 on, which one with a drifting wave 4th is rotatably connected.

Four in relative to the axis of rotation of the wheel 2 Pinions that are preferably regularly spaced from one another in the circumferential direction each have a pinion toothing 1 on and are each with a respective wave 3 non-rotatably connected. The axes of rotation of these shafts 3 however, are not parallel to the aborted shaft 4th but in each case skewed to the axis of rotation of the driven shaft 4th arranged.

The pinion teeth 1 mesh with the toothing of the wheel 2 .

Each of the waves 3 is non-rotatable and coaxial with a rotor shaft of a respective electric motor 21st connected.

The electric motors 21st each have two bearings for pivoting their respective rotor shaft. The first of the two bearings, especially the one from the electric motor 21st The bearing closest to the driven pinion is in a respective bearing flange of the respective electric motor 21st recorded.

The bearing flanges of all electric motors 21st are with a holding part 20th connected.

The contact surface is preferably between the holding part 20th and each of the bearing flanges is flat and each part of one and the same plane.

But since the rotor shaft axes of the electric motors 21st are skewed to each other, this is achieved by the bearing flange of each of the electric motors 21st is wedge-shaped.

In this way, the same bearing flange is on each of the electric motors 21st usable. Within the plane, the individual respective bearing flanges are rotated by 90 ° or an integral multiple of 90 ° with respect to one another, the angle of rotation being a rotation around the normal of the plane and / or the axis of rotation of the driven shaft 4th is provided.

The wall thickness of the respective bearing flange increases in a first, to the axis of rotation of the rotor shaft of the electric motor belonging to this respective bearing flange 21st perpendicular direction monotonously, in particular strictly monotonously.

In a direction perpendicular to this first direction, which is also perpendicular to the axis of rotation of the rotor shaft of the electric motor belonging to this respective bearing flange 21st is aligned, the wall thickness of the bearing flange is constant.

The bearing flange is therefore shaped like a wedge. The first direction is the wedge direction. The wall thickness is always parallel to the direction of the axis of rotation of the shaft 3 of the pinion measured.

The transmission according to the invention is therefore a summing transmission in which at least two, preferably four, pinions mesh with one wheel. The envelope is the toothing of the wheel 2 a truncated cone section. The envelope of the toothing of a respective pinion, in particular of a respective pinion toothing 1 , is also a truncated cone section. The cone tips and truncated cone axes of rotation of the two truncated cone sections are skewed to the axis of rotation of the wheel 2 .

In this way, the invention achieves a high degree of efficiency, a high power density, low noise emissions and economical production.

The cross axis angle, i.e. the angle between the axis of rotation of the respective pinion and the axis of rotation of the wheel, is not 90 ° but is between 10 ° and 13 °.

The cone angle of the envelope of the toothing of the wheel 2 differs from the cone angle of the envelope of the pinion toothing 1 .

The toothing of the wheel 2 has a helix angle and is therefore helical. The pinion teeth 1 also has a helix angle, so it is helical. However, the helix angle, in particular the main spiral angle, is the pinion toothing 1 larger, in particular by 1.5 ° to 6 ° larger, in particular by 3 ° larger, than the helix angle, in particular the main spiral angle, of the wheel 2 .

The helix angle of the wheel 2 is preferably between 25 ° and 60 °. The total overlap during tooth meshing thus exceeds 2.5.

The wheel 2 is narrower than a respective pinion, in particular than a respective pinion toothing 1 .

The wheel 2 as well as the pinions can be produced from a case-hardened steel.

The ones from the electric motors 21st driven and with the teeth of the wheel 2 The pinion teeth in mesh are all identical.

In further exemplary embodiments according to the invention, the pinion teeth 1 in the circumferential direction from one another not evenly, but unevenly spaced. The circumferential angle between a first pinion and a pinion which follows in the circumferential direction to the first next adjacent pinion thus differs from the circumferential angle between the second and a third pinion which follows in the circumferential direction to the second next adjacent pinion.

The electric motors lead during operation 21st their respective performance needs-based.

In addition, depending on the power required, one or more motors must be switched off 21st enables. It is essential that the engines 21st be used differently in partial load operation. The number of poles and / or the rated power of the electric motors 21st is preferably different.

In further exemplary embodiments according to the invention, instead of four, the axis of rotation of the wheel 2 in the circumferential direction regularly spaced pinion gears more or less based on the axis of rotation of the wheel 2 provided in the circumferential direction regularly spaced pinion teeth.

In further exemplary embodiments according to the invention, rectangular bearing flanges are used instead of the wedge-shaped bearing flanges and the respective contact surfaces in the holding part are used for this 20th accordingly inclined to the axis of rotation of the wheel 2 shaped. The holding part is then preferably 20th not in one piece, but in several parts, in particular the division of the number of pinion teeth 1 corresponds. When running after 2 would be the holding part 20th divided into four equal parts, each of the parts being of the same type, that is to say structurally identical, and each having an inclined contact surface for receiving the respective bearing flange.

So each of the parts takes one of the electric motors 21st and is arranged rotated by 90 ° or an integral multiple of 90 °, in particular the angle of rotation being measured around the axis of rotation of the output shaft.

As in 3 shown, the bearing flanges are shown in further exemplary embodiments according to the invention 30th shaped similar to the wedge-shaped bearing flanges. The contact surface is to the holding part 31 towards each level and all contact surfaces of the holding part 31 lie in the same plane. A contact surface of the bearing flanges 30th to the engine 21st towards is also made flat, so that the normal to this flat surface is aligned parallel to the axis of rotation of the rotor shaft of the electric motor 21st .

The normals of the contact surfaces to the holding part 31 indicate a non-vanishing angle to the axis of rotation of the rotor shaft of the respective electric motor 21st . The bearing flange 30th thus has a housing that resembles a section of a tube bent at an angle, which is the holding part 31 provided for; flat contact surfaces connects with those to the engine 21st provided, level contact surfaces.

The bearing flange 30th is shaped according to a curved pipe section which has a square collar, in particular a square flange, at its two end regions. This protrudes radially, the radial direction at the first end area on the axis of rotation of the rotor shaft and at the other end area on the normal of the common to the holding part 30th facing contact surfaces.

List of reference symbols

1

Pinion teeth

2

wheel

3

wave

4th

drifting wave

20th

Holding part

21st

Electric motor

30th

flange

31

Holding part

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was 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.

Patent literature cited

• US 2011/0209573 A1 [0002]
• DE 20212935 U1 [0004]
• DE 102017000304 B3 [0005]
• DE 102016118877 A1 [0006]

Claims (15)

Transmission with a wheel having a toothing and pinion gears each having a pinion toothing, in particular wherein the wheel is mounted rotatably about an axis of rotation and / or the pinions are mounted rotatably about a respective axis of rotation, the pinion teeth being in engagement with the toothing and / or mesh, characterized in that the respective axis of rotation of the pinion, in particular pinion toothing, is each aligned skew to the axis of rotation of the wheel. Gearbox after Claim 1 , characterized in that the pinion teeth are unevenly spaced from one another in the circumferential direction with respect to the axis of rotation of the wheel. Gearbox after Claim 1 , characterized in that the pinion gears are evenly spaced from one another in the circumferential direction in relation to the axis of rotation of the wheel. Transmission according to one of the preceding claims, characterized in that the wheel is a spur gear, in particular wherein the toothing is a spur gear toothing. Transmission according to one of the preceding claims, characterized in that the envelope of the toothing of the wheel is a truncated cone, in particular the rotational body determined by the maximum radial distance relative to the rotational axis of the wheel being a truncated cone, the rotational symmetry axis of the rotational body being the rotational axis of the wheel . Transmission according to one of the preceding claims, characterized in that the envelope of the pinion toothing is a truncated cone, in particular wherein the rotational body determined by the maximum radial distance with respect to the axis of rotation of the pinion toothing is a truncated cone, the rotational symmetry axis of the rotational body being the rotational axis of the pinion toothing. Transmission according to one of the preceding claims, characterized in that the angle between the axis of rotation of the pinion toothing and the axis of rotation of the wheel is between 10 ° and 13 °. Transmission according to one of the preceding claims, characterized in that the cone angle of the truncated cone of the wheel differs from the cone angle of the truncated cone of the pinion toothing 1. Transmission according to one of the preceding claims, characterized in that the toothing of the wheel has a first helix angle, i.e. is helical, wherein the pinion toothing has a second helical angle, i.e. is helical, the second helix angle being greater than the first helix angle, in particular where the first helix angle differs from the second helix angle by 1.5 ° to 6 °, in particular by 3 °, in particular where the first helix angle is between 25 ° and 60 °, in particular where the total overlap exceeds 2.5. Transmission according to one of the preceding claims, characterized in that the wheel is designed to be narrower than the respective pinion, in particular than the respective pinion toothing. Transmission according to one of the preceding claims, characterized in that the wheel and the pinion are made from a case-hardened steel. Transmission according to one of the preceding claims, characterized in that the pinion toothings are driven by electric motors and are in engagement with the toothing of the wheel, the pinions being made identical to one another, in particular all being made identical to one another. Transmission according to one of the preceding claims, characterized in that the transmission has a holding part which is connected to a housing part of the transmission, wherein a shaft of the transmission, in particular the output shaft of the transmission, is rotatably supported by means of a bearing, which is accommodated in the holding part or housing part, each pinion being non-rotatably connected to a rotor shaft of a respective electric motor, which is rotatably mounted relative to a bearing flange of the respective electric motor, in particular wherein the respective bearing flange receives a respective bearing of the respective rotor shaft, in particular wherein the respective bearing flange is made in one piece, in particular in one piece, with each bearing flange being connected to the holding part, wherein the contact surfaces between the holding part (31) and the bearing flanges (30) are flat and are arranged in a common plane, each bearing flange (30) being shaped so as to correspond to a wedge-shaped and / or such a curved pipe section, - that the rotor shaft of the respective electric motor has a non-vanishing angle to the normal of the plane - and / or that a contact surface between the respective bearing flange (30) and a housing part of the respective electric motor is made flat and has a non-vanishing angle to the plane, in particular with each bearing flange (30) is shaped as a bent pipe section, which has a square collar on its end region directed towards the holding part (31), in particular a square collar which protrudes radially in relation to the axis of rotation of the rotor shaft of the electric motor, and which on its end region facing the housing part of the electric motor (21) directed end area a quadra table collar, in particular a square, relative to the axis of rotation of the rotor shaft radially protruding collar. Gearbox after Claim 13 , characterized in that the holding part is made in one piece, in particular in one piece. Gearbox according to one of the Claims 3 to 12 , characterized in that the transmission has a holding part which is connected to a housing part of the transmission, wherein a shaft of the transmission connected to the wheel in a rotationally fixed manner, in particular the output shaft of the transmission, is rotatably mounted by means of a bearing which is received in the holding part or housing part each pinion is rotatably connected to a rotor shaft of a respective electric motor, which is rotatably mounted relative to a bearing flange of the respective electric motor, wherein the holding part is multi-part, in particular multi-part, so has interconnected parts, the parts to each other structurally identical, in particular identical, with each part being connected only to a single respective bearing flange and a respective contact surface between the respective part and the respective bearing flange being encompassed by a plane whose normal to the axis of rotation of the rotor shaft of the respective Bearing flange associated electric motor is aligned in parallel.

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