DE202021003344U1 - Gearbox with gravity rotor - Google Patents

Abstract

Transmission (1) for the variable coupling of a movement with a higher number of harmonics to a movement with a lower number of harmonics, with a rotor (2) which can rotate in relation to a stationary stator (3), characterized in that the stator (3) has an elliptical track (15) and the rotor has a plurality of telescopically extendable cantilevers which can be rotated about a common axis of rotation (6) which is eccentrically displaced or eccentrically adjustable in relation to the center of the elliptical track (15) of the stator (3) and at least one roller each at their free ends (1$) that rolls along the elliptical track (15) of the stator (3).

Description

The invention relates to a transmission for the variable coupling of a movement with a higher number of harmonics to a movement with a lower number of harmonics, comprising a rotor which can revolve in relation to a stator which is immovable relative thereto.

In various applications, it is desirable to design a transmission for coupling two different movements in such a way that, for example, a movement with a high number of harmonics can be converted into a movement with fewer harmonics, so that the force of a drive device that acts unevenly or asymmetrically can be converted into a uniform movement, see above that, for example, by means of an electric generator, a uniform generation of energy is possible.

For example, in some cases there is an uneven or one-sided or asymmetrical force application, and it is necessary to harmonize this in order to generate a more even speed, so that, for example, a coupled electric generator supplies a constant voltage or an optimally sinusoidal AC or three-phase voltage or .

The invention is not only limited to the geared coupling between two rotary movements; for example, there is often a desire in the art to couple reciprocating motion, such as a piston, to rotary motion, such as a crankshaft.

On the other hand, asymmetries as described can also be desired. For example, a conventional internal combustion engine works with four strokes - intake, compression, power stroke, exhaust. In the fourth stroke, the combustion gases can only be completely expelled if the piston moves all the way up in the cylinder, while this is not desirable in the compression stroke because the pressure in the compressed gases would then be too high. It is therefore desirable to control the piston in such a way that it performs a slightly smaller stroke on each compression stroke than on the exhaust stroke. In the case of sophisticated engines or test benches, this different stroke should even be adjustable.

The disadvantages of the prior art described result in the problem that initiated the invention of developing a generic transmission in such a way that a movement with few harmonics is converted into a movement with a lot of harmonics, or vice versa.

The solution to this problem is that the inner side of the stator follows an elliptical path and the rotor has several telescopically extendable arms which can be rotated about a common axis of rotation that is eccentrically adjusted or eccentrically adjustable to the center of the elliptical stator and at their free ends carry at least one roller each, which rolls along the elliptical inside of the stator.

Whereas, for a star revolving within a circular stator, the arms are either constant in length as long as the star is at the center of the circular stator, or periodically vary in harmonic fashion when the star center is eccentric to the center of the circular stator a different behavior is found in a stator with an elliptical track for the arms of a star.

bzw.: $${\mathrm{\omega }}_{\text{R}}={\mathrm{\omega }}_{\text{K}}*{\text{U}}_{\text{K}}/{\text{U}}_{\text{R}}=4*{\mathrm{\omega }}_{\text{K}}*{\text{U}}_{\text{S}}/{\text{U}}_{\text{R}}.$$

In the case of a circular stator, the circumference U _K is divided by a concentric star into four equal segments U _S = ¼ * U _K . If the star continues to rotate by 90° in a period of time t ₀ , each arm of the star covers the same path U _S and the rotational speed ω _R of each roller with the circumference U _R at the end of such an arm is: $${\text{u}}_{\text{K}}:{\text{u}}_{\text{R}}={\mathrm{\omega }}_{\text{R}}:{\mathrm{\omega }}_{\text{K}},$$

or.: $${\mathrm{\omega }}_{\text{R}}={\mathrm{\omega }}_{\text{K}}*{\text{u}}_{\text{K}}/{\text{u}}_{\text{R}}=4*{\mathrm{\omega }}_{\text{K}}*{\text{u}}_{\text{S}}/{\text{u}}_{\text{R}}.$$

If the circle is now deformed into an ellipse in such a way that in one position all four arms are in contact with the ellipse, those two segments U _S of the ellipse which run approximately parallel to the main axis of the ellipse become flattened compared to the arc of the circle and are therefore shorter , while the other two segments U _S of the ellipse, which run approximately parallel to the minor axis of the ellipse, assume a course that is more curved than the circular arc and therefore become longer. Consequently, the rotational speed ω _R of the rollers has two maxima and two minima during one rotation of the star. A harmonic wave is superimposed on an average speed of the rollers, namely a harmonic wave with twice the speed of the star. If, in such an arrangement, the bearing of the star, around which it rotates, is displaced eccentrically relative to the center of the ellipse along its main axis, one of the two longer circumferential segments U _S becomes larger and the other smaller. It follows that the speed harmonics of a roll during a full rev hung of the star reaches two local maxima, namely when the arm in question is located exactly on the main axis. However, these two maxima are not the same size, but different. The difference between these two maxima is dependent or approximately proportional to the eccentricity of the bearing of the star relative to the center of the ellipse, and is therefore adjustable.

The movement rich in harmonics generated in this way can be used for various purposes. It can also be converted into a proportional stroke, for example via a centrifugal mechanism.

If—as the invention further provides—it is not the star that rotates, but the ellipse surrounding it, the fundamental oscillation can be eliminated from the arrangement. In a similar way, the variable distance between the roller and the center of the star can be eliminated by not mounting the star in a fixed position, but by mounting a roller at the end of a telescopic arm. A transmission according to the invention can therefore also be used in the context of a motor with a different stroke, or also in the context of a generator, for example a power generator. Furthermore, it can be advantageous--in particular with regard to gravity--to make the arrangement such that the ellipse surrounding the star is arranged in a vertical plane.

It has proven to be advantageous for the telescopic element, which carries at least one roller, to be solidly constructed on one or more telescopically extendable extension arms and to be slidably guided within the tubular telescopic element arranged further inwards. In this way, a backlash-free telescopic arrangement can be implemented, which enables a long service life.

Further advantages result from the fact that on one or more telescopically extendable extension arms, the telescopic element carrying at least one roller is pretensioned by the force of a spring into its maximum extended position. This ensures that the rollers always have optimal contact with the elliptical raceway of the stator.

The invention can be further developed in such a way that on one or more telescopically extendable booms in the area of its free end, an axis of rotation running transversely to its longitudinal direction is rotatably mounted, which carries a roller at each of its two ends. By using a pair of rollers connected to one another via an axis of rotation instead of a single roller, the result is a completely symmetrical bearing without any lateral forces and thus optimum guidance of the rollers within the plane of the ellipse.

Another advantageous measure is that a fork is provided on one or more telescopically extendable booms in the region of their free end, each with one of two mutually aligned bearings for rotatably bearing accommodation of a rotary axis for at least one roller. A double bearing of the axis of rotation for at least one roller within two planes spaced apart from one another also serves to ensure that the eccentric rollers are rotated with as little play as possible, with the aim of achieving the longest possible service life.

The invention also provides that the radially inner telescopic elements of the boom are fixed to a hub body with their rear ends. Such a hub body, preferably common to all telescopic booms, is used for at least partial mutual compensation of changing forces, in that oppositely directed forces are introduced into the hub body from telescopic booms lying diametrically opposite one another.

The invention recommends that the hub body be mounted or fixed on a central axle or be integrated with a central axle, or that two aligned, central axle stubs be provided on the hub body. As a result, the rotary movement of the star of telescopic booms relative to the elliptical path can be taken out of the path plane and coupled there, for example, with a drive or output.

Furthermore, the central axle or the pair of aligned, central axle stubs can be mounted on a common bearing device via one or more bearings.

The invention is further characterized by an adjusting device, with which the bearing device can be adjusted relative to the stator having the elliptical path and can be locked in different positions.

In addition, it has proven useful for the adjustment device for the bearing to have a straight guide device, which allows the bearing device for the central axle or the pair of aligned, central axle stubs to be adjusted along a straight line.

Finally, it corresponds to the teaching of the invention that the guide device is aligned with respect to the stator in such a way that the straight line ent along which an adjustment of the bearing device for the central axle or the pair of aligned, central axle stubs is possible, coincides with the main axis of that ellipse along which the inner side of the stator runs.

• 1 den Rotor eines erfindungsgemäßen Getriebes in einem Schnitt entlang einer Ebene, die von der Drehachse des Rotors lotrecht durchsetzt ist;
• 2 einen Querschnitt durch die 1 entlang der Linie II - II, wobei eine Verstelleinrichtung für eine exzentrische Verstellung des Rotors gegenüber dem Stator wiedergegeben ist;
• 3 eine andere Ausführungsform eines erfindungsgemäßen Rotors in einer Ansicht gemäß 2, jedoch abgebrochen dargestellt;
• 4 den Rotor aus 1 innerhalb eines Stators, dessen Innenseite einem elliptischen Verlauf folgt, in einer ersten Drehstellung des Rotors gegenüber dem Stator, wobei sich zwei von vier Teleskopauslegern auf der Hauptachse einer Ellipse befinden, dem die Innenseite des Stators folgt, während die übrigen beiden Teleskopausleger auf der Nebenachse dieser Ellipse liegen;
• 5 den Rotor aus 1 innerhalb eines Stators, dessen Innenseite einem elliptischen Verlauf folgt, in einer zweiten Drehstellung des Rotors gegenüber dem Stator, welche gegenüber der ersten Drehstellung gemäß 4 um etwa 45° verdreht ist, so dass sich alle vier Teleskopausleger etwa auf den Winkelhalbierenden zwischen der Haupt- und Nebenachse derjenigen Ellipse befinden, welcher die Innenseite des Stators folgt;
• 6 den Verlauf der Drehzahl einer Rolle um ihre eigene Achse während der Drehung des Rotors bei einer exzentrisch eingestellten Position der zentralen Achse gegenüber der Stator-Ellipse; sowie
• 7 den Verlauf der Drehzahl einer Rolle um ihre eigene Achse während der Drehung des Rotors bei einer im Zentrum des Stators eingestellten Position der zentralen Achse.

Further features, details, advantages and effects based on the invention result from the following description of a preferred embodiment of the invention and from the drawing. This shows:

• 1 the rotor of a transmission according to the invention in a section along a plane through which the axis of rotation of the rotor passes perpendicularly;
• 2 a cross section through the 1 along the line II - II, wherein an adjustment device for an eccentric adjustment of the rotor relative to the stator is reproduced;
• 3 another embodiment of a rotor according to the invention in a view according to FIG 2 , but shown broken off;
• 4 the rotor off 1 inside a stator, the inner side of which follows an elliptical shape, in a first rotational position of the rotor relative to the stator, with two of the four telescopic arms being located on the main axis of an ellipse which the inner side of the stator follows, while the other two telescopic arms are on the minor axis of this ellipse lying;
• 5 the rotor off 1 within a stator, the inside of which follows an elliptical course, in a second rotary position of the rotor relative to the stator, which relative to the first rotary position according to 4 is rotated by about 45°, so that all four telescopic arms are located approximately on the bisector between the major and minor axes of that ellipse which follows the inside of the stator;
• 6 the history of the rotational speed of a roller about its own axis during the rotation of the rotor at an eccentrically adjusted position of the central axis with respect to the stator ellipse; as
• 7 the history of the rotational speed of a roller about its own axis during the rotation of the rotor with a position of the central axis set in the center of the stator.

A transmission 1 according to the invention can be used for the variable coupling of a movement with a higher number of harmonics to a movement with a lower number of harmonics and comprises a rotor 2 which can rotate in relation to an immovable stator 3 . In general, the stator 3 forms a housing surrounding the transmission 1, in which the rotor 2 is rotatably mounted. However, the terms rotor and stator in this context are not to be regarded as prejudice for the assembly of this transmission 1 . Of course, the stator 3 can also be mounted so that it can rotate, and the rotor 2 could also be fixed non-rotatably on a chassis or the like, so that the functions of the rotor 2 and the stator 3 are effectively reversed.

In 1 the drawing shows the rotor 2 of the transmission 1 taken by itself. A hub body 4 can be seen, with a central recess 5 for receiving an axis of rotation 6.

gegeneinander versetzt, so dass der Rotor 2 sich in einem indifferenten Gleichgewichtszustand befindet, wenn die Längen aller Ausleger 7 gleich sind, wie dies in 1 dargestellt ist. Wäre dagegen einer der Ausleger 7 - bspw. in 1 der rechte - länger als der gegenüberliegende - also in 1 der linke - so würde sich auf der einen Seite ein Übergewicht gegenüber der anderen Seite ergeben und damit ein Drehmoment, welches bestrebt ist, den Rotor 2 in eine Richtung zu drehen, damit der längere Ausleger 7 eine tiefere Position einnimmt als der kürzere.Arranged on the hub body 4 of the rotor 2 are a plurality of, generally n, in the example shown four, arms 7 striving outwards from the axis of rotation 6 in the form of spokes, each at the same central angle $$\mathrm{\phi }=360°/\text{n}$$

mutually offset, so that the rotor 2 is in an indifferent state of equilibrium when the lengths of all the cantilevers 7 are the same, as is the case in 1 is shown. If, on the other hand, one of the booms 7 - e.g. in 1 the right one - longer than the opposite one - that is, in 1 the left - this would result in an overweight on one side compared to the other side and thus a torque which tends to turn the rotor 2 in one direction so that the longer boom 7 assumes a lower position than the shorter one.

The arms 7 on the hub body 4 of the rotor 2 are designed to be telescopically extendable. For this purpose, each boom 7 consists of two mutually displaceable parts, namely a hollow, profile-shaped outer body 8, in the cavity 9 of which a preferably solid inner body 10 is guided with almost no play, but still easily displaceable. This is preferably achieved in that the outer cross section of the inner body 10 corresponds to the inner cross section of the outer body 8 .

Although the lengths of the inner body 10 and the outer body 8 can be substantially the same size; however, the inner body 10 is offset radially outwards relative to the outer body, so that a compression spring 11 , preferably a spiral compression spring, is accommodated within the cavity 9 .

This compression spring 11 is supported with its radially inner end on the hub body 4, and since its intrinsic length is greater than the radial extension of the free cavity 9, it presses the inner body 10 with its radially outer end to the outside.

How to 1 and 2 can further be seen, the inner body 10 carries in the region of its outer end a bearing 12 for an axis of rotation 13, which extends from the inner body 10, starting parallel to the axis of rotation 6 in both directions. In the region of each end of this axis of rotation 13 a roller 14 is arranged so as to be rotatable about the axis of rotation 13 .

In 2 is also indicated that the rollers 14 of the rotor 2 mounted on the arms 7 in turn roll on a preferably elliptical, concave track 15 on the inside of the stator 3 . Due to the radially displaceable inner body 10 , the rollers 14 are always able to follow this concave track 14 and are reliably pressed against the inside of the track 15 by the compression springs 11 . Since two rollers 14 are always seated at the end on a common axis of rotation 13, which in turn is mounted approximately centrally on the inner body 10, this assembly is constructed completely symmetrically and is therefore completely free of transverse forces.

In order to absorb any tangential forces that may occur within the main plane of the rotor 2, the outer body 8 of the extension arm 7 can also be connected to the hub body 4 by a ring 16 as additional stabilization, with the ring 16 preferably having twice the radius of the hub body 4.

At the in 2 illustrated embodiment, the rollers 14 as well as the track 15 are smooth, ie toothless. However, both - ie rollers 14 as well as track 15 - could be provided with a circumferential toothing, and due to the mutual engagement of these two teeth a slippage between the rollers 14 and the track 15 would then be excluded.

In the 3 a further development of the invention is shown, in which the radially outer end of the inner body 10 is designed as a fork 17, with two preferably disc-shaped legs 19 connected to one another by a kind of yoke 18, in each of which a bearing 20, in particular a ball bearing, is preferably Storage of the eccentric axis of rotation 13 is arranged. This axis of rotation in turn carries a roller 14 at both ends, both of which are supported on the track 15 . In the area between the two legs 19 of the fork 17, a gear wheel 21 can also be arranged, which is preferably non-rotatably fixed to the axis of rotation 13, while the two rollers 14 can also be rotatably mounted on the axis of rotation 13, if necessary. In this case, the two rollers 14 support the axis of rotation 13 relative to lateral, flat elements of the track 15, while the toothed wheel 21 meshes with a row of teeth arranged between these two lateral track elements. The advantage is that the meshing, toothed elements - i.e. the rotor-side gear 21 on the one hand and the row of teeth on the stator-side raceway on the other - are not directly pressed together, but rather at an optimal distance from one another and therefore roll smoothly on each other.

how to get in 1 can continue to see, the directions of rotation 22, 23 of the central axis of rotation 6 and the eccentric axes of rotation 13 are directed in opposite directions.

while out 1 only the structure of the rotor 2 emerges, is in 2 the overall arrangement, consisting of rotor 2 and stator 3, can be seen.

It can be seen in particular that the central axis of rotation 6 of the rotor 2 is not immovably fixed, but is mounted on a type of carriage 24 which can be adjusted relative to the stator 3, in particular in the direction of the main axis of the ellipse of the stator 3.

For the purpose of such an adjustable arrangement, the bearings 25 of the central axis of rotation 6 can each be arranged on a type of shield or leg 26, which extend parallel to the main plane of the rotor 2 and can in turn be connected to one another by a yoke-like bracket 27, so that in cross section according to 2 roughly the shape of a U.

The eccentricity of the originally concentric, central axis of rotation 6 of the rotor 2 can be adjusted by this yoke-like bracket 27 being displaceably guided relative to the housing of the transmission 1 along a guide parallel to the main axis of the ellipse of the stator 3 .

In 4 indicates how the rotor 2 behaves within a stator 3 with an elliptical track 15 .

In this case, according to the arrangement 4 the - not shown carriage 24 - set eccentrically to the center of the elliptical track 15, i example shown shifted to the left. Due to the compression springs 11 are still all rollers 14 on the track 15 at.

4 shows a moment of rotation 22 where two diametrically opposite cantilevers 7 lie straight in the main axis 28 of the ellipse and two other cantilevers 7 just perpendicular are oriented towards it. It can be seen that one of the two cantilevers is 7-in 4 the right one - on the main axis 28 of the ellipse is drawn out further than the other. The other two arms 7 perpendicular to the main axis 28 of the ellipse, on the other hand, are extended telescopically to the same extent at this moment.

In 5 the same arrangement is shown at a later point in time, at which the rotor 2 compared to the arrangement 4 rotated further by a rotation angle of 45°. Now, two adjacent outriggers 7 are mutually symmetrical to the main axis 28 of the ellipse. It can be seen that the two right outriggers 7 are extended telescopically to the same extent, but are significantly longer than the two left outriggers 7, which are also extended telescopically to the same extent .

When the rotor 2 rotates in this state concentric with the stator 3, so

Now consider the situation again 4 , but with a concentric arrangement of the rotor 2 in relation to the stator 3, i.e. with the two cantilevers 7 on the main axis 28 of the ellipse being exactly the same length, it can be seen that the other two cantilevers 7 then lie exactly on the minor axis of the ellipse, the force definition is shorter than the main axis 28 of the ellipse. In this case, therefore, two adjacent cantilevers 7 are not of the same length as in 5 , but two diametrically opposite cantilevers 7.

The course of the length of a boom 7 is in 6 shown. During a complete rotation of the rotor 2, this fluctuates between two equally large maximum values and two equally large minimum values, the length of course always being positive.

If now - starting from this symmetrical state - the rotor 2 is eccentrically adjusted by a small amount, but not as far as in 4 , the two cantilevers 7 parallel to the main axis 28 of the ellipse are still longer than the two cantilevers 7 perpendicular thereto. However, the cantilever length increases at one maximum, while it decreases at the other maximum, which in 6 with the two arrows 29, 30 is shown. This leads to a curve as shown in 7 is shown. It can be seen that one maximum is now higher than the following maximum.

If the eccentricity is increased more and more, then at some point the length of the shorter boom 7 on the main axis 28 of the ellipse becomes shorter than the two booms 7 perpendicular to that. 4 shows the eccentricity at which the shorter boom 7 on the main axis 28 of the ellipse is just as long as the two perpendicular booms 7.

From this eccentricity limit, the behavior changes according to the curve 7 again, because now there is no longer a harmonic with twice the periodicity per one complete revolution of the rotor 2, i.e. with two maxima and two minima per complete revolution of the rotor 2, but only the fundamental wave with the same periodicity, ie with one maximum and a minimum per complete revolution of the rotor 2.

In other words, by changing the eccentricity of the rotor 2 in relation to the stator 3, not only can the amplitude of a harmonic be changed, in particular reduced, but this harmonic can be reduced to such an extent that the resulting length function of a cantilever 7 does not have a double periodicity more shows, but just a simple one.

The invention can also be further developed such that the rollers 14 or gears 21 do not roll on the concave inside of the elliptical track 15, but rather on the convex outside of the elliptical track 15 of the stator 3. For this purpose, the rotor 2 can be positioned relative to the stator Track 15 are offset laterally and embrace them outside.

On the other hand, the compression springs 11 must then be replaced by tension springs.

If the rollers 14 roll outside the raceway 15, so to speak on the convex outside thereof, their roller diameter is not limited by the dimensions of the stator 3. It is also possible, for example, to design the arrangement in such a way that the circumference of a roller 14 is twice the circumference of the convex track 15 of the ellipse. Then a roller 14 performs only a quarter turn between two maxima.

In this case, a type of rotor blade could be arranged on an eccentric axis of rotation 13 of one or all rollers 14 on the outside, ie at one or both ends, such that its blade plane is spanned by the axis of rotation 13 . This rotor blade plane could, for example, at a vertex 31, 32 of the main axis 28 of the ellipse - for example at the 4 right vertex 32 - be aligned parallel to that, and is then at the other vertex 31, 32 of the elliptical main axis 28 perpendicular to it - in 4 i.e. at the left vertex 31.

If in this case a flow medium flows with a uniform flow direction - for example in 4 from top to bottom - such a rotor blade would be in the left-hand apex 31 parallel to this flow, so it would not produce any force or torque on the central axis of rotation 6 there, while the relevant rotor blade on the right-hand apex 32 is aligned transversely to this flow direction and therefore a maximum torque on the central axis of rotation 6 performed. In this way, a transmission 1 according to the invention can be used to convert energy into rotational energy, which can then be tapped off at the axis of rotation 6 and, for example, converted into electrical energy in a generator connected thereto.

Reference List

1

transmission

2

rotor

3

stator

4

hub body

5

recess

6

axis of rotation

7

boom

8th

outer body

9

cavity

10

inner body

11

compression spring

12

storage

13

axis of rotation

14

role

15

career

16

ring

17

fork

18

yoke

19

leg

20

camp

21

gear

22

direction of rotation

23

direction of rotation

24

sleds

25

storage

26

leg

27

hanger

28

main axis

29

arrow

30

arrow

31

vertex

32

vertex

Claims (11)

Transmission (1) for the variable coupling of a movement with a higher number of harmonics to a movement with a lower number of harmonics, with a rotor (2) which can rotate in relation to a stationary stator (3), characterized in that the stator (3) has an elliptical track (15) and the rotor has a plurality of telescopically extendable cantilevers which can be rotated about a common axis of rotation (6) which is eccentrically displaced or eccentrically adjustable in relation to the center of the elliptical track (15) of the stator (3) and at least one roller each at their free ends (1$) that rolls along the elliptical track (15) of the stator (3). Transmission (1) after claim 1 , characterized in that the telescopic element (10) carrying at least one roller (14) is solidly constructed on one or more telescopically extendable extension arms (7) and is slidably guided within the tubular telescopic element (8) arranged radially further inwards. Transmission (1) after claim 1 or 2 , characterized in that on one or more telescopically extendable arms (7) the at least one roller (14) carrying telescopic element (10) is biased by the force of a spring (11) in the direction of its maximum extended position. Transmission (1) according to one of Claims 1 until 3 , characterized in that on one or more telescopically extendable arms (7) in the region of its free end, a rotation axis (13) running transversely to its longitudinal direction is rotatably mounted, which carries one or both ends of a roller (14). Transmission (1) according to one of the preceding claims, characterized in that a fork (17) is provided on one or more telescopically extendable arms (7) in the region of its free end, each with one of two aligned bearings (20) for rotatably bearing Accommodating an axis of rotation (13) for at least one roller (14). Transmission (1) according to one of the preceding claims, characterized in that the radially inner telescopic elements (8) of the arms (7) are fixed with their rear ends on a hub body (4). Transmission (1) after claim 6 , characterized in that the hub body (4) is mounted or fixed on a central axle (6) or is integrated with a central axle (6) or that two aligned, central axle stubs are provided on the hub body (4). Transmission (1) after claim 7 , characterized in that the central axle (6) or the pair of mutually aligned, central axle stubs is mounted on a bearing device (25). Transmission (1) after claim 8 , characterized by an adjustment device (24), with which the bearing device (25) relative to the stator (3) can be adjusted and locked in different positions. Transmission (1) after claim 9 , characterized in that the adjusting device for the adjusting device (24) has a straight guide device which allows an adjustment of the bearing device (25) for the central axis of rotation (6) or the pair of aligned, central stub axles along a straight line. Transmission (1) after claim 10 , characterized in that the guide device is aligned with respect to the stator (3) in such a way that the straight line along which an adjustment of the bearing device (25) for the central axis of rotation (6) or the pair of aligned, central stub axles is possible with coincides with the main axis (28) of that ellipse along which the raceway (15) of the stator (3) runs.

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