CN118274094A

CN118274094A - Gear and method for manufacturing same

Info

Publication number: CN118274094A
Application number: CN202311777305.9A
Authority: CN
Inventors: C·杜曼斯基; S·贝格尔; F·莱特纳; W·希普尔
Original assignee: Miba Sinter Austria GmbH
Current assignee: Miba Sinter Austria GmbH
Priority date: 2022-12-30
Filing date: 2023-12-22
Publication date: 2024-07-02
Also published as: AT526358B1; AT526358A4; DE102023135815A1

Abstract

The invention relates to a gear wheel and a method for producing the same, comprising a first radially inner annular element (2) and a second radially outer annular element (3), the second radially outer annular element being produced with an outer toothing (5), the first radially inner annular element being produced with a plurality of radially outwardly projecting first projections (9), the second radially outer annular element being produced with a plurality of radially inwardly projecting second projections (11), the first projections being produced with first flanks (25, 26) and the second projections being produced with second flanks (16, 17), recesses (13) being formed between the second projections, the first projections of the first radially inner annular element being arranged in the recesses, an elastomeric element (20) being arranged between the first radially inner annular element and the second radially outer annular element, the first flanks and/or the second flanks being machined with a rolling tool and/or a generating tool. The gear has improved vibration damping properties.

Description

Gear and method for manufacturing same

Technical Field

The invention relates to a method for producing a gear wheel comprising a first radially inner annular element and a second radially outer annular element, the second radially outer annular element being produced with an external toothing, the first radially inner annular element being produced with a plurality of first projections projecting radially outwards and the second radially outer annular element being produced with a plurality of second projections projecting radially inwards, each first projection being produced with a first flank extending between first axial end faces and each second projection being produced with a second flank extending between second axial end faces, a recess being formed between each second projection, the first projections of the first radially inner annular element being arranged in each recess, and at least one elastomer element being arranged between the first radially inner annular element and the second radially outer annular element.

The invention also relates to a gear comprising a first radially inner annular element and a second radially outer annular element, the second radially outer annular element having an outer toothing, the first radially inner annular element having a plurality of radially outwardly projecting first protrusions and the second radially outer annular element having a plurality of radially inwardly projecting second protrusions forming recesses between the second protrusions, the first protrusions of the first radially inner annular element projecting into the recesses, each first protrusion having a first flank extending between first axial end faces and each second protrusion having a second flank extending between second axial end faces, and at least one elastomeric element being arranged between the first radially inner annular element and the second radially outer annular element.

Background

In order to avoid vibration excitation when torque is transmitted by means of the gears, it is known from the prior art to use elastically deformable elements. AT501915A4 describes a device for transmitting torque in a rotationally elastic manner between a shaft and a gearwheel supported on the shaft, which gearwheel forms a toothed ring and a hub, wherein rotational vibrations occurring between the toothed ring and the hub are damped by an elastomer intermediate layer between mutually opposite flank surfaces of mutually engaging claws.

A meshing assembly is known from DE102009058378A1, which comprises a first gear wheel and a second gear wheel, which meshes with the first gear wheel. The first gear includes: an inner ring having an axis of rotation; an outer ring arranged coaxially with the rotational axis of the inner ring and having an outer toothing into which the second gearwheel engages with a corresponding toothing, the engagement between the first gearwheel and the second gearwheel being effected solely by the outer ring; at least one elastic element which is arranged between the inner ring and the outer ring, via which the outer ring is supported radially relative to the inner ring, and in a non-loaded state in which no torque is transmitted between the first gear and the second gear, the outer toothing and the corresponding toothing are elastically preloaded or clamped radially against each other.

Other such gears in which the hub component is connected with the ring gear via an elastic element are known from patent documents AT514590A4, AT516397A4, AT514570A4 and AT520740 A4.

Disclosure of Invention

The object of the invention is to provide an improved vibration-damped gear.

The object of the invention is achieved by the method mentioned at the outset, according to which the first flanks of the first projections of the first radially inner annular element and/or the second flanks of the second projections of the second radially outer annular element are provided with a rolling tool (Walzwerkzeug) and/or a generating toolAnd processing.

The object of the invention is furthermore achieved by the gear wheel mentioned at the outset in that the first flanks of the first projections of the first radially inner annular element and/or the second flanks of the second projections of the second radially outer annular element are roll-machined and/or are machined by a generating method.

It is advantageous here if the flanks of the projections are processed by roll-in (Walzbearbeitung) or by a generating methodThe manufacturing error of the gear can be reduced. This in turn allows to increase the accuracy of the dimensions of the gap between the protrusions in which the at least one elastomeric element is arranged. The elastomeric elements or elastomeric element components disposed between the projections are thus subjected to a more uniform preload. Therefore, the rigidity value of the gear or the rigidity value of the meshing assembly having two gears meshing with each other (one gear is configured according to the present invention) can be set in advance with high accuracy. The rolling or forming process also has a cost advantage here compared to other processes for increasing the precision of the component.

In order to further improve this effect, it may be provided according to an embodiment of the invention that the first projection of the first radially inner annular element and/or the second projection of the second radially outer annular element are/is formed by means of a strong scraping toothIs manufactured.

Alternatively or in addition to the strong scraping teeth, in order to reduce errors when sintering the projections, an embodiment according to the invention may provide that the first projection of the first radially inner annular element and/or the second projection of the second radially outer annular element are calibrated with a rolling tool. The corresponding cost advantages in the manufacturing method of the gear can also be achieved by using a rolling tool.

According to a further embodiment of the invention, it can be provided that the first projection of the first radially inner annular element and/or the second projection of the second radially outer annular element are formed in the form of cycloidal teeth, in particular involute teeth. On the one hand, these tooth shapes can be machined more simply by means of rolling tools or generating cutters. On the other hand, such tooth shapes offer the following possibilities: the stiffness is modified by modifying the or each tooth accordingly. Thus, by varying the engagement angle or the inclination angle specifically on the first or second projection, a stiffness characteristic can be influenced, which can be formed, for example, progressively or linearly. In addition, the dependence of the torsional stiffness on the radial stiffness and on the axial stiffness or the overturning stiffness can thus be changed/influenced.

To further improve or influence these effects, embodiments according to the invention may provide that:

The first projection of the first radially inner annular element and/or the second projection of the second radially outer annular element are/is constituted in the form of a straight toothing or a helical toothing; and/or

The cycloidal teeth are manufactured with or have a joint angle between 0 ° and 90 °; and/or

The helical teeth are manufactured with an inclination angle of between 0 ° and 45 °, or with such an inclination angle.

According to a further embodiment of the invention, it may be provided that the at least one elastomer element is configured to contour a first flank of a first projection of the first radially inner annular element and/or a second flank of a second projection of the second radially outer annular element. It is thus possible that the error reduction of the first and/or second annular element is also transmitted to the elastomeric element, so that the adjustability of the stiffness of the gear can be further improved.

According to a further embodiment of the invention, it can be provided that a plurality of elastomer elements are provided in order to improve the reliability of the gear.

In this case, according to one embodiment, it can be provided that the plurality of elastomer elements are arranged only on the first flanks of the first projections of the first radially inner annular element and on the second flanks of the second projections of the second radially outer annular element. It is thus possible to allow errors in the tip region or root region of the first and second projections of the two ring elements, so that the machining effort of the individual ring elements can be reduced.

Drawings

For a better understanding of the invention, the invention is explained in more detail with the aid of the following figures.

The simplified schematic diagrams are as follows:

FIG. 1 shows an embodiment of a gear in an exploded view and an oblique view;

Fig. 2 shows two ring elements of the gear wheel according to fig. 1 in the assembled state;

fig. 3 shows two ring elements of the gear of fig. 1 in an assembled state and with mounted elastomeric elements;

FIG. 4 shows an oblique view of an elastomeric element;

FIG. 5 shows a partial view of one embodiment of a first annular element;

fig. 6 shows a partial view of another embodiment of a gear.

Detailed Description

It is first to be determined that in the differently described embodiments identical components are provided with the same reference numerals or the same component names, and that the disclosure contained throughout the specification may apply in meaning to identical components having the same reference numerals or the same component names. The orientation description selected in the description, such as up, down, sideways, etc., also relates to the figures directly described and depicted, and these orientation descriptions may be applied in meaning to new orientations as the orientation changes.

In fig. 1 an embodiment of a gear 1 is shown. Figures 2 to 3 show the components of the wheel 1 respectively.

The gear wheel 1 comprises a first radially inner annular element 2, a second radially outer annular element 3 and optionally a cover element 4. The first radially inner annular element 2 may also be referred to as hub component and the second radially outer annular element 3 may also be referred to as ring gear, since the first radially inner annular element 2 is intended to receive a shaft or the like, not described, and the second radially outer annular element 3 has an external toothing 5. Through this external toothing 5, the gear wheel 1 can be meshed for torque transmission with another gear wheel, for example a transmission gear wheel, in order to be able to transmit torque accordingly.

The first radially inner annular element 2 is arranged radially below the second radially outer annular element 3, in particular completely below the external toothing 5, seen in the radial direction 6. Preferably, the first radially inner annular element 2 is arranged entirely inside the second radially outer annular element 3, although the hub region 7 of the first radially inner annular element 2 may be wider in the axial direction 8 than the second radially outer annular element 3.

The first radially inner annular element 2 and/or the second radially outer annular element 3 are preferably made of a metallic material, for example steel, preferably of a sintered material, for example sintered steel. However, other metallic materials may be used for the first radially inner annular element 2 and/or the second radially outer annular element 3, and the first radially inner annular element 2 and/or the second radially outer annular element 3 may also be made of at least two different metallic materials. It is also conceivable that the first radially inner annular element 2 and/or the second radially outer annular element 3 are made of at least one polymeric plastic.

The first radially inner annular element 2 has a plurality of first protrusions 9 projecting outwards in the radial direction 6. The first projections 9 are provided on the radially outer circumferential surface of the hub member 7, in particular connected in one piece therewith. Preferably, these first protrusions 9 are evenly distributed over the circumference of the hub 7 in the circumferential direction 10 of the gear wheel 1.

In addition, the first radially inner annular element 2 has a recess, in particular a bore, extending in the axial direction 8. Thus, the first radially inner annular element 2 may be provided on a shaft or other element not described, such as an unbalance element or the like. The unbalance element itself may have a recess, in particular a hole, for arrangement on the shaft.

The second radially outer annular element 3 has a plurality of second projections 11 which project in the radial direction 6 and which, unlike the first projections 9, are not arranged projecting outwardly but rather projecting inwardly. The second projection 11 is provided on the inner circumferential surface 12 of the second radially outer annular element 3, in particular in one-piece connection therewith. Preferably, the second projections 11 are also arranged uniformly distributed over the circumference of the circumferential surface 12 in the circumferential direction 10 of the gear wheel 1.

For the sake of completeness, it is mentioned that the bottom sides of the first and second projections 9, 11 are not formed straight, but curved, due to the rounded shape of the gear wheel 1.

Between the second projections 11, recesses 13 are formed in the circumferential direction 10. Also, recesses 14 are formed between the first protrusions in the circumferential direction 10. The recesses 13, 14 are arranged such that each first projection 9 is at least partially, in particular completely, received in a recess 13 between the second projections 11, and each second projection 11 is at least partially, in particular completely, received in a recess 14 between the first projections 9, as can be seen, for example, from fig. 2. By "completely" is meant here that the first protrusion 9 is slightly spaced apart from the circumferential surface 12 and the second protrusion 11 is slightly spaced apart from the hub part 7, such that a relative rotatability of the first annular element 2 with respect to the second annular element 3 in the circumferential direction 10 is possible.

The first protrusion 9 is narrower in the circumferential direction 10, i.e. has a smaller maximum length 15 (fig. 2), than the recess 13 in the circumferential direction 10. The length 15 is measured here at the same radial height as the length of the recess 13, in order to take into account the cross section of the first projection 9 which varies in the radial direction.

As a result of the first projection 9, which is narrower in the circumferential direction 10, the first projection 9 is arranged at a distance from the flanks 16, 17 of the second projection 11, which face in the circumferential direction 10 and extend between the axial end faces in the axial direction 8, gaps 18, 19 are formed, as can best be seen in fig. 2. A gap 18 and a gap 19 are thus formed next to each first projection 9 in the circumferential direction 10, so that the respective gap 18, 19 is thus formed on both sides of the first projection 9. Each first projection 9 therefore does not rest against either of the two side surfaces 16, 17 of the second projection 11 in this embodiment of the gear wheel 1.

An elastomer element 20 is arranged in each of these gaps 18, 19, as can best be seen in fig. 3. Each elastomeric element 20 is thus arranged between the first radially inner annular element 2 and the second radially outer annular element 3. The elastomer elements 20 are loosely inserted into the gaps 18, 19, i.e. they are neither connected to each other nor to the first radially inner annular element 2 and the second radially outer annular element 3, and therefore in particular are not glued or vulcanized thereon. However, each elastomeric element 20 (i.e. the preliminary stage for the elastomer) may be vulcanized in the gaps 18, 19, in which embodiment the elastomer formed is not adhered to the metal.

One such elastomeric element 20 is depicted in fig. 4.

The elastomeric element 20 is at least partially made of a rubber-elastic material such as (X) NBR (carboxylated nitrile rubber), HNBR (hydrogenated nitrile rubber), silicone rubber (VMQ), natural Rubber (NR), EPDM (ethylene propylene diene monomer), CR (neoprene), SBR (styrene butadiene rubber), etc., again mixtures of materials may be used.

By "at least partially" is meant that, for example, reinforcing elements such as fibers and/or filaments (e.g., composed of metal, plastic, natural fibers, etc.) or rods may be incorporated into the elastomeric element 20 in order to alter or adjust the stiffness of the elastomeric element. The elastomeric member 20 may also have a plurality of regions made of different rubber elastic materials from one another. Preferably, however, the elastomeric member 20 is made of only one rubber elastic material.

The elastomer element 20 of this embodiment of the gearwheel 1 is at least approximately cuboid in shape. But the elastomeric member 20 may have other shapes.

For a simpler installation of the elastomer element 20, it can be provided that a further cover element 21 is provided on the first radially inner annular element 2 or preferably on the second radially outer annular element 3 and is connected thereto, for example in a form-and/or force-and/or material-locking manner. The further cover element 21 may also be formed in one piece with the first radially inner annular element 2 or the second radially outer annular element 3. The further cover element 21 covers the recesses 13 at least partially, in particular completely, on one side of the gearwheel 1 in the axial direction 8, so that the elastomer element 20 can rest on the further cover element 21 during installation.

When all elastomer elements 20 are mounted, i.e. inserted, they can be covered at least partially, preferably completely, on the second side in the axial direction 8 with the covering element 4. The cover element 4 may be connected to the first radially inner annular element 2 or the second radially outer annular element 3. The connection can be made detachable (for example with screws) or material-locking (for example by welding) depending on the application of the gearwheel 1.

Overcompensation of the shrinkage stress can also be performed in the elastomer rail by the cover elements 4 and 21, so that the gear is free of play (in hysteresis testing).

In a simpler embodiment of the gear wheel 1, only the gap 18 or only the gap 19 can be formed between the first and the second projection 9, 11. The elastomer element 20 is thus present on only one of the two flank surfaces 16, 17 of the second projection 11. On the other side, the first and second projections 9, 11 may at least approximately abut each other. Although this embodiment is not preferred, it may also be employed in the following applications: in these applications, the gear 1 operates in only one direction of rotation.

As already set forth hereinabove, the gear wheel 1 may have a first radially inner annular element 2, a second radially outer annular element 3, at least one connecting element and a plurality of elastomeric elements 20. However, the gearwheel 1 may also consist of only these components.

It is possible that the elastomer element 20 has a length in the axial direction 8 which is equal to or greater than the length of the gaps 18, 19 in this direction.

In order to be able to support or simplify the compression of the elastomer element 20, it can be provided according to a further embodiment of the gearwheel 1 that the elastomer element 20 has at least one outwardly arched side surface 22, as can be seen from fig. 4. The side surfaces 22 are in particular convexly curved. The curvature may be formed on a side surface 22 pointing in the axial direction 8. The two side surfaces 22 of the elastomer element 22 can be formed in a curved manner, as is depicted in fig. 4.

Alternatively or in addition thereto, the further side surfaces and/or the bottom surface and/or the top surface of the elastomeric element 20 may also be arched.

At least some of the outer surfaces of the individual elastomeric elements 20 may also be formed so as to be inwardly arched. In particular, the curvature can be formed concavely.

The elastomeric member 20 may have a recess 24. The compressibility of the elastomeric element 20 may thus be affected or simplified.

It can furthermore be provided that the edge of the elastomer element 20 can be provided with a rounded portion, as can be seen in particular from fig. 4.

As with the second projection 11, the first projection 9 also has first flanks 25, 26 extending between the first axial end faces.

The first projection 9 and/or the second projection 11 may be formed in the form of teeth, as can be seen for example in fig. 1. The teeth may be formed (as described in the figures) in the form of straight teeth or in the form of helical teeth.

Provision is made for the first flanks 25, 26 of the first protuberance 9 of the first radially inner annular element 2 and/or the second flanks 17, 18 of the second protuberance 11 of the second radially outer annular element 3 to be roll-machined or machined. In particular, it can be provided that the first projection 9 of the first radially inner annular element 2 and/or the second projection 11 of the second radially outer annular element 3 are formed in the form of cycloidal teeth. Cycloidal teeth are known per se from the prior art for gears, so that a conceptual explanation of cycloidal teeth is omitted. In a preferred embodiment, the first projections 9 and/or the second projections 11 are configured as involute teeth, as this is shown in fig. 1 only on the first projections 9 for the embodiment with an involute, and in fig. 6 on both the first projections 9 and the second projections 11. But there are also possibilities: only the second projections 11 are formed as involute teeth.

The cycloidal teeth are produced with a rolling tool or a generating tool, so that preferably the flanks 25, 26 of the first projection 9 and/or the flanks 16, 17 of the second projection 11 are identically formed.

Shaping can be achieved in particular by means of strong scraping teeth, but also by means of slotting teethGear shavingAnd so on. As an alternative or in addition to this, it is also possible, in particular when the first annular element 2 and/or the second annular element 3 are manufactured by powder metallurgy: the primary shaping is effected by means of a female die and the first projection 9 and/or the second projection 11 are calibrated by rolling with a squeeze gear.

According to one embodiment of the gearwheel 1, it can be provided that the cycloidal toothing has an engagement angle of between 0 ° and 90 °, in particular between 5 ° and 60 °, for example between 8 ° and 45 °. The term "engagement angle" is as commonly employed for gears. Hereby, the contact point of the two tooth surfaces moves on a straight line, the so-called engagement stroke, during the entire engagement. The angle by which the joining stroke is inclined with respect to the vertical line (in the case where the central axis of the first annular element 2 or the second annular element 3 and the central axis of the rolling tool or the generating tool extend through a common horizontal line) is the joining angle. The engagement angle corresponds to the flank angle of the reference profile.

In the case of the tooth formation of the first projection 9 and/or of the second projection 11 being designed as a helical tooth, it can be provided that the helical tooth has an inclination angle of between 0 ° and 45 °, in particular between 5 ° and 35 °, for example between 8 ° and 25 °. Once both the first projection 9 and the second projection 11 are configured as helical teeth, the two helical teeth preferably have the same angle of inclination. However, embodiments with different inclination angles are also possible, in which case it is preferred that the inclination angles differ from one another by not more than 10 °, in particular not more than 8 °, for example not more than 5 °.

The term "inclination angle" means the angle the projection 9 or 11 has with respect to the axial direction 8. Accordingly, an inclination angle of 0 ° means a straight tooth portion.

Preferably, the first projection 9 and/or the second projection 11 are symmetrically formed in cross section.

In the embodiment of the gearwheel 1 according to fig. 1 to 4, the elastomer element 20 has a shape which differs from the shape of the first flanks 25, 26 of the first projection 9 and the shape of the second flanks 16, 17 of the second projection 11, so that the elastomer element 20 rests at least in the unloaded state only partially against the first flanks 25, 26 of the first projection 9 and the second flanks 16, 17 of the second projection 11. According to another embodiment of the gear wheel 1, however, it may be provided that the elastomer element 20 contours the first flanks 25, 26 of the first protuberance 9 of the first radially inner annular element 2 and/or the second flanks 16, 17 of the second protuberance 11 of the second radially outer annular element 3, and thus has, in particular, a shape that is inverse to the shape of the cycloidal teeth of the first protuberance 9 and/or the second protuberance 11. This is shown in fig. 5 for the first protrusion 9 and in fig. 6 for the first and second protrusions 9, 11.

There are additionally possibilities within the scope of the invention: only one single elastomer element 20 extending continuously over the entire circumference is provided between the first annular element 2 and the second annular element 3, as can also be seen by means of the partial views of the gear wheel 1 in fig. 5 and 6. The first and second ring elements 2, 3 are arranged at a distance from each other such that a gap is formed between the first and second projections 9, 11, which gap is continuous around the circumference and is filled with the elastomer element 20. For this purpose, the gap can be filled, for example, by a preliminary phase of the elastomer for the elastomer element 20 and then vulcanized, or a corresponding shaping can be carried out outside the gap and the finished elastomer element 20 can be fitted into the gap.

It is also possible to vulcanize the elastomeric element 20 onto the first and second protrusions 9, 11, i.e. onto their first flanks 25, 26 and second flanks 16, 17, and to join them. The connection of the elastomeric element 20 to the first and second protrusions 9, 11 is generally possible within the scope of the invention, even if embodiments are possible in which the elastomeric element 20 is present separately in each gap 18, 19. The connection can be achieved by means of vulcanization or by means of the use of an adhesive. Alternatively or additionally, form-locking connections can be used in addition to the material-locking connections.

By vulcanization or by vulcanization in the preparation phase of the elastomer between the two ring elements 2, 3 (in the gap already mentioned), a further reduction of the errors can be achieved, so that in the final effect an embodiment of the gear 1 can be produced which has no stiffness change or a stiffness change of up to 5%.

It is to be noted here that the gap can be formed over the entire circumference with a thickness which remains constant in the radial direction. But there are also possibilities: in particular, when the elastomer element 20 is arranged only in the gaps 18, 19, a radial distance of at most 0.5mm is formed between the top and bottom of the first and second protrusions 9, 11. The distance between the first and second flanks 25, 26, 16, 17 may be at least 1.5mm at the narrowest point and may be at most 7.5mm at the widest point.

It may further be provided that the first flanks 25, 26 and/or the second flanks 16, 17 have a surface roughness Ra of between 0.2 μm and 12.5 μm. These surfaces may be relatively rough, so that the attachment or connection of the at least one elastomeric element 20 to the first or second annular element 2, 3 may be improved.

The examples show or illustrate several embodiments of the gear wheel 1, it being noted here that a combination of the individual embodiments with each other is also possible.

For reasons of regularity, it is finally pointed out that the gear 1 or its components are not necessarily to scale for a better understanding of the structure.

List of reference numerals

1. Gear wheel

2. Annular element

3. Annular element

4. Covering element

5. External tooth part

6. Radial direction

7. Hub region

8. Axial direction

9. Protrusions

10. In the circumferential direction

11. Protrusions

12. Peripheral surface

13. Concave part

14. Concave part

15. Length of

16. Side wing surface

17. Side wing surface

18. Gap of

19. Gap of

20. Elastomer element

21. Covering element

22. Side surfaces

23. End face

24. Recess in the bottom of the container

25. Side wing surface

26. Side wing surface

Claims

1. A method for manufacturing a gear wheel (1) comprising a first radially inner annular element (2) and a second radially outer annular element (3), the second radially outer annular element (2) being manufactured with an outer toothing (5), the first radially inner annular element (2) being manufactured with a plurality of radially outwardly projecting first protrusions (9), and the second radially outer annular element (3) being manufactured with a plurality of radially inwardly projecting second protrusions (11), each first protrusion (9) being manufactured with a first flank (25, 26) extending between first axial end faces and each second protrusion (11) being manufactured with a second flank (16, 17) extending between second axial end faces, a recess (13) being formed between each second protrusion (11), the first protrusions (9) of the first radially inner annular element (2) being arranged in each recess, and at least one elastomer element (20) being arranged between the first radially inner annular element (2) and the second radially outer annular element (3), characterized in that the first protrusions (9) of the first radially inner annular element (2) are manufactured with a first flank (25, 26) and the second flank (16, 17) of the second radially inner annular element (3) being rolled into a second flank or a tool.

2. Method according to claim 1, characterized in that the first protrusion (9) of the first radially inner annular element (2) and/or the second protrusion (11) of the second radially outer annular element (3) are manufactured by means of strong scraping teeth.

3. Method according to claim 1 or 2, characterized in that the first protrusions (9) of the first radially inner annular element (2) and/or the second protrusions (11) of the second radially outer annular element (3) are calibrated with a rolling tool.

4. A method according to any one of claims 1 to 3, characterized in that the first protrusion (9) of the first radially inner annular element (2) and/or the second protrusion (11) of the second radially outer annular element (3) are constituted in the form of cycloidal teeth, in particular involute teeth.

5. The method of claim 4, wherein the cycloidal teeth are manufactured with an engagement angle between 0 ° and 90 °.

6. Method according to any one of claims 1 to 5, characterized in that the first protrusion (9) of the first radially inner annular element (2) and/or the second protrusion (11) of the second radially outer annular element (3) are manufactured as helical teeth.

7. The method of claim 6, wherein the helical teeth are manufactured with a tilt angle between 0 ° and 45 °.

8. Method according to any one of claims 1 to 7, wherein the at least one elastomeric element (20) is configured to profile a first flank (25, 26) of a first protrusion (9) of the first radially inner annular element (2) and/or a second flank (16, 17) of a second protrusion (11) of the second radially outer annular element (3).

9. Method according to any one of claims 1 to 8, characterized in that a plurality of elastomeric elements (20) are provided.

10. A method according to claim 9, wherein the plurality of elastomeric elements (20) are provided only on the first flanks (25, 26) of the first protrusions (9) of the first radially inner annular element (2) and the second flanks (16, 17) of the second protrusions (11) of the second radially outer annular element (3).

11. A gear wheel (1) comprising a first radially inner ring element (2) and a second radially outer ring element (3), the second radially outer ring element (3) having an outer toothing (5), the first radially inner ring element (2) having a plurality of radially outwardly projecting first protrusions (9) and the second radially outer ring element (3) having a plurality of radially inwardly projecting second protrusions (11), a recess (13) being formed between each second protrusion (11), the first protrusions (9) of the first radially inner ring element (2) projecting into each recess, the first protrusions (9) having first flanks (25, 26) extending between first axial end faces and the second protrusions (11) having second flanks (16, 17) extending between second axial end faces, and at least one elastomer element (20) being arranged between the first radially inner ring element (2) and the second radially outer ring element (3), characterized in that the first flanks (25, 26) of the first protrusions (2) and/or the second flanks (16, 17) of the first radially inner ring element (2) are rolled or the second flanks (3) are machined or formed by a second machining process.

12. Gear (1) according to claim 11, characterized in that the first projection (9) of the first radially inner annular element (2) and/or the second projection (11) of the second radially outer annular element (3) are constituted in the form of straight or helical teeth.

13. Gear (1) according to claim 11 or 12, characterized in that the first projection (9) of the first radially inner annular element (2) and/or the second projection (11) of the second radially outer annular element (3) are constituted in the form of cycloidal teeth, in particular involute teeth.

14. Gear (1) according to claim 13, characterized in that said cycloidal teeth have an engagement angle between 0 ° and 90 °.

15. Gear (1) according to any one of claims 12 to 14, characterized in that said helical teeth have an inclination angle between 0 ° and 45 °.

16. Gear wheel (1) according to any one of claims 11 to 15, characterized in that said at least one elastomeric element (20) contours a first flank (25, 26) of a first projection (9) of the first radially inner annular element (2) and/or a second flank (16, 17) of a second projection (11) of the second radially outer annular element (3).

17. Gear (1) according to any of claims 11 to 16, characterized in that a plurality of elastomeric elements are provided.

18. Gear wheel (1) according to claim 17, wherein said plurality of elastomeric elements (20) are provided only on the first flanks (25, 26) of the first protrusions (9) of the first radially inner annular element (2) and on the second flanks (16, 17) of the second protrusions (11) of the second radially outer annular element (3).