CN106051109B - Driving element - Google Patents

Abstract

Drive element (50) for a gear mechanism, in particular a coaxial gear mechanism, having a plurality of teeth which are guided radially in a tooth carrier and are mounted so as to be movable, said teeth being mounted with their tooth roots on a pivot segment and with their tooth tips in the tooth portions, wherein the drive element (50, 150) comprises: a cam disk (20) having a contour (22) for supporting the rolling bodies, on which contour the pivot section is mounted so as to be movable in the circumferential direction; a bearing section (46) arranged axially next to the cam disk (20); a hole circle (52) arranged in the bearing section (46).

Description

Driving element

Technical Field

The invention relates to a drive element and a method for using a drive element.

Background

From the prior art, transmission mechanisms are known which comprise several teeth which are mounted in a tooth carrier so as to be radially displaceable. For driving the teeth, a profiled drive element, such as a cam disk, is used. The teeth engage in the teeth, so that a relative movement between the toothed carrier and the teeth can be caused. The relative movement between the toothing and the teeth is in this case smaller by at least one order of magnitude than the movement of the drive element with the profile. In this way, a high transmission can be obtained, an example of such a transmission mechanism being disclosed in DE 102007011175 a 1.

However, known gear mechanisms of this type of construction are partially inflexible with respect to their integration in the drive train, i.e. the combination of the motor and the gear mechanism or mechanisms. There is a need for a flexible integration of a transmission mechanism of the type described above in an assembly or a drive train.

Disclosure of Invention

The object of the present invention is to provide a transmission or a component or assembly of a transmission that is improved in comparison to the devices known from the prior art, wherein, in particular, an improved flexibility is to be achieved or the production is to be simplified. The object of the invention is also to specify a method for using such a device.

This object is achieved with a drive element according to the following and a method for using a drive element according to the following: a drive element for a gear mechanism with a plurality of teeth which are guided radially in a tooth carrier and are mounted so as to be movable, said teeth being mounted with their tooth roots on a plurality of pivot segments and with their tooth tips acting into the tooth portions, wherein the drive element comprises: a cam disk with a contour for supporting a plurality of rolling bodies, on which a plurality of pivoting segments are mounted so as to be movable in the circumferential direction, a bearing section for receiving a bearing, which is arranged axially next to the cam disk, wherein the bearing section extends in the axial direction such that the entire outer circumference of the bearing section receives a bearing inner ring of the bearing, a bore circle, which is provided in the bearing section. A transmission with a drive element and with a plurality of teeth which are guided radially in a tooth carrier and are mounted so as to be movable, said teeth being mounted with their tooth roots on a plurality of pivot segments and with their tooth tips in the teeth, wherein the pivot segments are mounted with a plurality of rolling bodies on a cam disk of the drive element. An assembly with a drive element according to the invention and with a mount which comprises a mount support section with an outer diameter corresponding to the outer diameter of the support section of the drive element and/or comprises a mounting hole circle with a diameter corresponding to the diameter of the hole circle of the drive element. A drive train with a gear mechanism according to the invention and a drive device, the output element of which is connected to the drive element of the gear mechanism by means of a mounting, wherein a bearing inner ring of a bearing is fastened between a mounting step of the mounting and a step of the drive element. Use of a drive element according to the invention for connecting a transmission comprising the drive element to a mounting. Advantageous modifications and embodiments result from the following and from this description: the cam disk is designed in a hollow manner, wherein the inner diameter of the cam disk is smaller than the diameter of the bore circle; the cam disc comprises an edge for axially supporting the rolling body; the drive element is constructed in a monolithic manner; the drive element is hardened; a step for fixing the bearing is provided between the bearing section and the cam disk at the outer circumference of the drive element; the transmission is a coaxial transmission, the mount at the outer periphery comprises a mounting step for fixing the bearing, the mounting step being connected to the mounting support section; the mounting is hollow; the assembly is provided with a driving device, and a driven element of the driving device is connected with the mounting part or is implemented in a single body mode with the mounting part; the assembly has a membrane for increasing the coefficient of friction, which is arranged to be inserted between the mounting part and the drive element.

One aspect of the invention relates to a drive element for a gear mechanism, in particular a coaxial gear mechanism, having a plurality of teeth which are guided radially in a tooth carrier and are mounted so as to be movable, said teeth being mounted with their tooth roots on a pivot segment and with their tooth tips in the tooth portions, wherein the drive element comprises: a cam disk with a contour for supporting the rolling bodies, on which the pivot section is mounted so as to be movable in the circumferential direction; a bearing section, which is arranged axially in parallel with the cam disk; a hole circle, which is arranged in the bearing section.

A further aspect relates to a gear unit having a drive element in one of the exemplary embodiments described here and having a plurality of teeth which are guided radially in a tooth carrier and are mounted so as to be movable, said teeth being mounted with their tooth roots on the pivot segments and with their tooth tips in the teeth, wherein the pivot element is mounted with rolling bodies on a cam disk of the drive element.

Another aspect relates to an assembly with a drive element and a mount in one of the exemplary embodiments described herein, the mount comprising a mount support section with an outer diameter corresponding to the outer diameter of the support section of the drive element and/or a mounting hole circle with a diameter corresponding to the diameter of the hole circle of the drive element.

A further aspect relates to a drive train with a transmission and a drive device in one of the embodiments described herein, the driven element of which is connected to the drive element of the transmission by means of a mounting, wherein a bearing inner ring of a bearing is fixed between the mounting step of the mounting and the step of the drive element.

Another aspect relates to the use of a drive element in one of the exemplary embodiments described herein for connecting a transmission comprising the drive element to a mount.

Embodiments of the present invention relate particularly to coaxial transmission mechanisms. In general, a typical gear mechanism or a gear mechanism provided for the drive element of the described embodiments comprises, as drive element, a profiled, internally situated cam disk and a hollow wheel with an internally situated toothed section or an externally situated drive element with an internally situated profiled section and an internally situated gear wheel or an internally situated toothed rack which provides a toothed section for the externally situated drive element in this case. The embodiment relates to a linear drive for converting a rotation into a linear movement.

The toothing is typically a circumferential toothing. The teeth or the tooth tips of the teeth act into the teeth, wherein the teeth are typically mounted so as to be linearly radially displaceable relative to the tooth carrier. Here, "linearly radial" generally means that there is a guide in the radial direction, which allows only one movement of the teeth in the radial direction. Typically, the tooth segment is linearly displaced in exactly one direction by the guide, which can be achieved, for example, by the tooth having a cross section which is always the same in the displacement direction for a specific path length, wherein the tooth carrier likewise has an opening for a tooth segment with an always identical cross section. Likewise, the teeth are correspondingly mounted in the tooth carrier so as to be displaceable in exactly one direction, typically in the direction of the longitudinal axis of the teeth. Furthermore, in the exemplary embodiment, the teeth are locked with respect to a rotational degree of freedom of the tooth carrier about the longitudinal axis of the gear mechanism. This can be achieved, for example, by linear guidance of the teeth in the radial direction in the tooth carrier. In this way, the teeth rotate with the tooth carrier about the longitudinal axis of the transmission, but do not rotate relative to the tooth carrier.

In a typical embodiment of the transmission according to the invention, at least a part of the teeth is designed to be inflexible. The term "inflexible" is understood here typically in the art, that is to say that the bending of the tooth is so small that it is at least substantially unimportant to the kinematics of the transmission mechanism, because of the rigidity of the material of the tooth. The non-flexible teeth include, in particular, teeth made of a metal alloy, in particular steel or a titanium alloy, a nickel alloy or another alloy. Furthermore, in particular, it is also possible to provide in the rotary device teeth which are formed from plastic and are not easily bent, in which transmission at least one of the following components is likewise made from plastic: a toothed section at the hollow wheel or the toothed wheel, a toothed carrier and a drive element. In a typical embodiment of the invention, the tooth carrier and the teeth are made of a metal alloy, or also additionally the toothing or additionally the drive element is made of a metal alloy. Such a gear mechanism offers the advantage that it is extremely torsionally stiff and can be highly loaded. A gear made of plastic offers the advantage that it has a low weight. The expression "stiff refers in particular to the bending stiffness around the transverse axis of the tooth segment. This means, in particular, that, when the tooth segment is considered as a beam, a flexural rigidity exists from the tooth root to the tooth tip, which flexural rigidity at least substantially excludes flexural deformations between the tooth root and the tooth tip. The flexural rigidity enables an extremely high loadability and torsional rigidity of the transmission.

In a typical embodiment, a pivot segment is arranged between the tooth and the contour, which pivot segment bears on a rolling bearing, which in turn is supported on the contour. An advantageous embodiment comprises a pivot section which is arranged between the profiled drive element and the respective at least one tooth. The pivot section enables tipping of the tooth relative to the profile or relative to the pivot section. Typically, at least two teeth are supported on the pivot segment. A plurality of teeth supported on the pivot segments are typically axially juxtaposed in sequence.

Typically, the tooth segment is loosely connected with the pivot segment. Here, "loose connection" preferably means that the tooth section is only set up on the pivot section, usually directly. Preferred pivot segments include a profile feature that discourages tooth slippage from the pivot segment or slippage of the pivot segment in at least one direction. It should be taken into account that the pivot segment is in this way held in its position in the circumferential direction relative to the tooth carrier by means of the radially and linearly guided teeth. Such a contour feature can be, for example, a bulge which acts into a depression. In this way it is ensured that the tooth segment does not slide past the pivot segment. This achieves that the pivot section is fixed in position to the teeth and relative movements between the tooth section and the pivot section in the circumferential direction are excluded. In this case, the contour features are preferably arranged such that a displaceability in the circumferential direction is blocked, so that slipping in the circumferential direction is avoided. However, in other embodiments, ball-and-socket, spherical or other projections can be provided which hinder the sliding of the pivot segments relative to the teeth.

The typical pivot segment achieves a segmented bearing. In typical embodiments, the pivot segment or other support segment, such as a plate, forms a segmented support. The segmented bearing offers the advantage that it can be adapted to the contour of the drive element and, on the other hand, permits reliable force transmission in the radial direction.

The pivoting segments preferably have edges facing each other with protrusions and depressions (e.g. corrugated or serrated). This offers the advantage that the needle rollers arranged below the pivot segments are reliably held in the space between the pivot segments and the drive element even with a small spacing between the pivot segments.

The loose connection between the tooth segment and the pivot segment offers the advantage of a simple construction. Here, "loose connection" means, in particular, that the teeth are not protected against being lifted from the pivot section. In transmissions of the generic type, the lifting of the teeth from the pivot section is generally prevented in that the teeth are guided by a toothing at the tooth tip.

An exemplary embodiment of the present invention includes a contoured drive element. The profile preferably has a non-circular or non-elliptical arch or curve. The non-circular or non-elliptical arch offers the advantage that any profile can be used, for example, to set different gear ratios. In the sense of the present application, the eccentric is also in the form of a circle or an ellipse, since, for the eccentric, only the axis of rotation does not correspond to the central axis of the circle, but a circle still exists. In a typical embodiment, the tooth carriers or teeth are of circular design. This provides the advantage of a simple geometry for the tooth carrier and the tooth. Typically, the force transmission takes place between the toothing and the toothing carrier on the slow side of the gear mechanism. This offers the advantage that the stroke for the transmission of force is extremely short, so that an extremely high stiffness can be achieved. Embodiments that satisfy these conditions are in non-terminal embodiments: a gear mechanism with an internally located cam disk as a drive and with an externally located hollow wheel with a toothing, wherein a tooth carrier is arranged between the hollow wheel and the cam disk; an outer contour at the hollow wheel for driving the radially movable teeth inwards towards a toothing arranged on a gear or rack.

The teeth and tines typically have curved edges. Examples of bends for the rim are cylindrical bends or bends in the form of logarithmic spirals. For a possible embodiment of the curvature in the form of a logarithmic spiral, reference is made to DE 102007011175 a 1. The curved surface offers the advantage that the active edge rests in a planar manner and not only in a linear or punctiform manner. In this way, an extreme stiffness in the transmission of forces between the toothing and the teeth is achieved.

In a typical embodiment, a bearing section is arranged axially adjacent to the cam disk, which bearing section has a bore circle. The hole circle is typically integrated in the bearing section, wherein in one embodiment the hole of the hole circle can also extend into the cam disk. In this way, a compact design is achieved. The support section is typically cylindrical or has a cylindrical section. Typically, the outer circumference of the bearing section is hardened and/or precisely manufactured. In this way, an exact bearing fit is achieved. In a typical embodiment, the entire drive element is hardened. In this way, it is possible to use hardened components to meet a plurality of requirements, namely a precise bearing fit and a hardened running surface for the rolling bodies of the bearings of the pivot segments on the cam disk.

In a typical embodiment, the cam disk is of hollow design, wherein the inner diameter of the cam disk is smaller than the diameter of the bore circle. The diameter of the bore circle is typically the diameter described by the center axis of the bore. In other embodiments, the inner diameter of the cam disk is smaller than the radial inward extent of the bore circle.

In a typical embodiment, the cam disk has an edge for axially supporting the rolling bodies. In this way, it is not absolutely necessary to provide additional axial securing for the rolling bodies.

Typical embodiments comprise a pivoting segment with a flat or stepless rolling or edge bearing surface or a surface facing the rolling bearing. This allows for a simple manufacture of the pivot section. Typically, the pivot segment can be supported on the rolling bodies with rolling bearing surfaces, wherein one edge bearing surface is arranged on each side in the axial direction at the pivot segment. The two edge bearing surfaces typically bear at least partially on the edge of the cam disk. In this way, the pivoting section is prevented from being secured against tipping about the axial direction relative to the transmission. The rolling bodies are typically needle rollers, but here also balls or other rolling bodies can be used.

Typically, the drive element is constructed in a monolithic manner. Typical drive elements include integrated embodiments of the cam disc together with the bearing section. Typically, the bearing section is embodied jointly in the immediate vicinity of the cam disk, integrally with the cam disk. In a typical embodiment, an additional shaft section can be provided on the opposite side of the cam disk, in particular opposite the bearing section, which shaft section is embodied integrally with the cam disk and the bearing section. Such shaft sections can, for example, have a toothed arrangement or be designed smoothly and make a clip connection or be connected to the rotor of the motor. In this way a compact embodiment is achieved.

In a typical embodiment, an intermediate section is provided between the bearing section and the cam disk. In other embodiments, the cam disk is proximate to the bearing section. Typically, a step is provided between the cam disc and the bearing section.

Typically, the bearing section has a smaller diameter than the smallest diameter of the cam disk or of the edge of the cam disk. In this way steps can be established.

In an embodiment, the step is established by means of an intermediate section, which is arranged between the cam disc and the bearing section. This enables a universal choice of the minimum radius of the cam disc.

Typically, the steps are arranged at the outer circumference of the drive element, wherein a typical step effects a fixing or clamping of a bearing, in particular a deep groove ball bearing or a rolling bearing in general, for example a rolling bearing in general or a rolling bearing with conical or cylindrical rolling bodies.

In one of the exemplary embodiments described herein, an exemplary embodiment of an assembly includes a drive element. Furthermore, such assemblies typically include a mount having a mounting support section with an outer diameter corresponding to the outer diameter of the support section of the drive element.

Typical embodiments of the mounting comprise a mounting hole circle with a diameter corresponding to the diameter of the hole circle of the drive element. By means of the same diameter selection for the bore circle, it is possible to connect the mounting to the drive element by means of a screw connection or a pin connection or generally by means of a fastening element. The same outer diameter of the bearing section enables the two components to be supported at the interface between the drive element and the mount by means of a bearing. Furthermore, the clamping or fixing of the bearing inner ring or of the bearing is effected on the one hand by the drive element and on the other hand by the mounting. This can simplify the structure and speed up assembly.

A typical mount of the present invention includes a mounting step at the outer periphery for securing a bearing. Typically, the mounting step is connected to the mounting support section. Typically, the mount is hollow. In a typical embodiment of the invention, the inner diameter of the hollow mounting corresponds to the inner diameter of the bearing section and/or the inner diameter of the cam disk. In typical embodiments, the mount and the drive element have a uniform inner diameter continuously. In an embodiment, it is also possible to provide the steps in the axial direction while maintaining the same inner diameter in the region of the interface between the drive element and the mounting in order to facilitate or ensure a central positioning of the mounting relative to the drive element.

A typical assembly includes a drive device, the driven element of which is connected to the mounting or is embodied in one piece with the mounting. Here, the drive is also to be understood in general terms in the exemplary embodiments, i.e., a "drive" can describe a device which is arranged on the drive side of the drive element of the gear mechanism, thus for example also describing a prestage, for example a planetary prestage which is in turn driven by a motor. In this example, the drive train is: the motor drives the planetary gear stage, which in turn drives the gear mechanism via a drive element. In other exemplary embodiments, the drive generally comprises a gear train stage, for example a planetary stage, in particular a hollow planetary stage or a planetary stage with a solid shaft, an angular stage, a toothed segment, a coupling adapter or generally a motor, in particular an electric motor or a hydraulic motor.

A typical assembly includes a diaphragm for increasing the coefficient of friction, the diaphragm being arranged or adapted to fit between the mounting member and the drive element. A typical diaphragm can be, for example, the model EK a Grip 10, a typical coefficient of friction of a diaphragm for increasing the coefficient of friction lying between 0.3 and 0.7, typically between 0.4 and 0.6. By means of the membrane, the friction fit between the mounting, i.e. for example the drive means and the drive element, can be improved.

In a typical drive train, there are elements of the assembly described here, in particular the drive mechanism is provided with a drive element in one of the typical embodiments described here, and there is a drive device, the driven element of which is connected with the drive element of the drive mechanism by means of a mounting. In a typical embodiment, the driven element is embodied integrally with the mounting. In other embodiments, a driven element, such as a motor shaft or an output shaft of a transmission, is coupled to the mount. Typically, a bearing inner ring of the bearing is fixed between the mounting step of the mounting and the step of the drive element. Such a drive train has a particularly compact design.

Drawings

The invention is explained in detail below with the aid of the attached drawings, which show:

FIG. 1 schematically illustrates an embodiment of a transmission in half cross-sectional view;

FIG. 2 shows a detail of the embodiment of FIG. 1 in a cross-sectional view;

FIG. 3 shows an embodiment of a drive element in a cross-sectional view;

FIG. 4 illustrates an embodiment of an assembly in cross-section;

FIG. 5 shows another embodiment of the assembly in cross-section, and FIG. 6 shows another embodiment of the assembly in cross-section.

Detailed Description

Exemplary embodiments of the invention are explained below with the aid of the drawings, wherein the invention is not limited to the exemplary embodiments, but the scope of the invention is determined by the inventive content stated in the description. In the description of the embodiments, the same reference numerals for the same or similar components may be used in different drawings and for different embodiments in order to make the description clearer. However, this does not mean that the respective components of the invention are limited to the variants shown in the embodiments.

One embodiment is shown in figure 1 in schematic half cross-sectional view. Fig. 1 shows a schematic illustration of a gear unit 1 in half section, which has a hollow wheel 3 with an internally encircling toothing 5. The other half of the gear mechanism 1 is constructed in a section similar to the illustrated section. The teeth 7 act into the teeth 5. For greater clarity, not every tooth 7 of fig. 1 is also provided with the reference numeral 7. Typically, two axially parallel toothed rings with a single tooth 7 are provided. The teeth 7 are mounted in a radially displaceable manner in a tooth carrier 11. For this purpose, the tooth carrier 11 has a radially oriented channel-like circular or groove-like opening, which ensures radial guidance of the teeth 7 in the tooth carrier 11. Due to the radial guidance in the opening, it is only possible for the tooth 7 to move radially along its longitudinal axis, in particular to exclude a rotation about the longitudinal axis of the gear unit 1 relative to the tooth carrier 11.

The longitudinal axis of the tooth typically describes the axis running from the tooth root to the tooth tip, while the longitudinal axis of the gear mechanism points in the direction of the axis of rotation of the gear mechanism. This can be, for example, the axis of rotation of the toothed carrier which can be used as a drive output or the axis of rotation of the cam disk.

The teeth 7 are driven by a drive element (see fig. 3) comprising a hollow cam disc 20. The cam disc 20 has a profile 22 for driving the teeth 7 in the radial direction. The contour 22 has a profile with two projections relative to the circumference, so that the respectively opposite tooth 7 enters the tooth gap of the tooth system 5 to the greatest extent. In other embodiments (see, e.g., fig. 6), the cam plate has three projections and in other embodiments the cam plate also has more projections.

In the transmission 1 with a rolling bearing shown in fig. 1, the teeth 7 are arranged on the contour of the drive element. The rolling bearing comprises rolling bodies 23, which are embodied in the exemplary embodiment as needle rollers.

In the embodiment of fig. 1, the cam disc is arranged internally and the toothing is arranged externally. In such an arrangement, the output is held at the toothed hollow wheel or at the tooth carrier, wherein the respective further element is fixed. In other embodiments, the drive element is arranged externally, i.e. externally to the tooth carrier, and the teeth are arranged internally. It is also possible to hold the output at an internal toothing or toothing carrier. The tooth carrier, in which the teeth are accommodated so as to be displaceable in a radially linearly guided manner, can also be described by its openings as a tooth cage.

The transmission 1 comprises a segmented bearing for the teeth 7. The segmented bearing comprises a pivot segment 24, which has a circular tooth bearing surface on the side facing the teeth 7 (see fig. 2) which forms a ridge on which the roots of the teeth 7 or, in the exemplary embodiments 2, 3 or 4, the teeth can be arranged next to one another in the axial direction of the gear mechanism 1. The elevations together with the corresponding recesses in the roots of the corresponding teeth 7 prevent slippage of the teeth 7 on the pivot segments 24.

The root joint for the tooth 7 is formed by the elevations, so that the tooth 7 can tilt relative to the pivot section 24, in order to ensure that there is no positive guidance. The pivot segments 24 are movable relative to one another in the circumferential direction, so that the spacing between the pivot segments 24 can be varied. In this way, the degrees of freedom in the direction of rotation of the pivot section 24 are also not locked. This achieves a largely positive guidance and largely positive radial drive of the pivot section 24 by the contour 22 of the cam disk 20. In order to reduce the frictional resistance between the contour 22 and the pivot section 24, the rolling bodies 23 are arranged as needle rollers. In other embodiments, balls or other rolling bearings are provided for supporting the pivot segments.

Fig. 1, 2 and 3 are described in connection with each other, wherein not all details are explained again and reference numerals have been identically used for identical components.

In fig. 2, a pivot section 24 of the transmission 1 of fig. 1 is shown. The pivot section 24 comprises a tooth bearing on the side of the pivot section 24 facing the teeth 7 in the transmission 1. The tooth support of the pivot section 24 comprises a tooth support surface 28 comprising a circular surface section for the respective at least one tooth 7. The circular surface section of the tooth contact surface 28 is designed in a circular manner here. The midpoint of the circle coincides with the rolling bearing surface 30 of the pivot segment 24. In this way, a respective axis of rotation 32 is provided for the teeth 7 supported on the pivot segment 24, which axis of rotation coincides with the rolling bearing surface 30. The rolling bearing surface 30 is the side of the pivot section 24 facing away from the teeth, i.e. the side facing the rolling bodies 23 or the cam disk 20. The rolling bearing surface 30 corresponds to a surface on which the rolling elements 23 roll.

The pivot segment 24 comprises a segment edge 34 which is forward in the direction of rotation and a segment edge 36 which is rearward in the direction of rotation. Here, the descriptions of "front" and "rear" are not meant in the sense of motion, but rather they describe two opposing sides of the pivot section 24. A typical gear mechanism can be driven in both directions, so that during operation, the front segment edge can also be the rear in the direction of movement in the loop, and the segment edge corresponding to this rear can also be the front.

At the transition from the rolling bearing surface 30 to the front segment edge 34 and to the rear segment edge 36, a respective rounded set-back or bevel 38 is provided. These setbacks or bevels facilitate the running-in of the rolling bodies 23, which can thus improve the quietness of operation of the respective pivot section 24.

In other embodiments, rounded transitions are provided in the region of the segment edges between the rolling contact surfaces and the flanks of the segment edges. These transitions can also be described as rounded retractions. Typically, a bevel or rounded setback is provided at least or only in the area of the protrusion.

In a typical embodiment, the pivot section is constructed without axial guidance. Since the edge takes over the guidance of the needle roller, axial guidance at the pivot joint is not absolutely necessary. In a typical embodiment, the protrusions are implemented point-symmetrically. Other embodiments are implemented with protrusions arranged axisymmetrically.

The pivoting section 24 of fig. 2 has an intermediate strip 40 which is located between the two dashed lines in fig. 2. Such an intermediate belt 40 is located below the tooth support surface 28. In front of and behind the intermediate belt 40, in the circumferential direction, there are in each case several projections which run parallel to the steps or in a zigzag pattern and in this way allow the action of the rolling bearing surfaces into one another.

In fig. 3, an embodiment of a drive element 50 is shown, which comprises the cam disk 20 of fig. 1. In the following description of fig. 3 to 6, the same reference numerals are used for the same elements and not all reference numerals or features are explained again in detail. In part, the same reference numerals are used for the same or similar components in different embodiments, so that, for example, fig. 6 shows another embodiment of the drive element (fig. 6: drive element 150), but which in part possesses the same features as drive element 50 of fig. 3. Moreover, not all features in all figures are provided with reference numerals, in part, to improve clarity.

The drive element 50 of fig. 3 comprises a cam disc 20 with a profile 22. The contour 22 comprises a circumferential running surface for the rolling bodies (see fig. 1) and has two projections over the entire circumference, wherein the two projections are shown in the section of fig. 3.

It is noted that fig. 6 shows an embodiment with three projections, wherein in the section of fig. 6 a projection is cut through on one side and the area of the contour with the smallest radius is cut through on the other side.

The cam disk 20 of the embodiment of fig. 3 comprises an edge 40, which provides an axial guide for the rolling bodies. The edge 40 can simultaneously be used as a mounting surface for an edge region or edge bearing region, so that tilting of the pivot segment is avoided. The pivot section can be held in its axial position by means of a thrust disk (which can be fastened, for example, to the tooth carrier). However, it is also possible to fasten a thrust disk (analafscheibe) on the drive element 50 or to make the edge 40 higher, so that it also surrounds the pivot section.

On one side of the cam disk 20, a center section 42 is connected in the axial direction, to which center section a step 44 is connected, and to which a support section 46 is connected. The bearing section 46 is cylindrical and has the same inner diameter as the intermediate section 42, the cam disk 20 and the shaft section 48. The shaft section 48 is arranged axially opposite the bearing section 46 relative to the cam disk 20 and is part of a drive element 50. Such a shaft section serves as a further bearing point and sealing face.

The drive element 50 is hardened. Furthermore, the drive element 50 is hardened and/or produced with great precision in the region of the bearing section 46 and the contour. The diameter and the surface correspond to the standard requirements for the bearing location, which are recommended by the bearing manufacturer, for example. In the region of the contour, a particular precision is achieved for the circular jump characteristic and for the force transmission in the gear mechanism.

In the region of the bearing section 46, the drive element 50 comprises a bore circle 52 which comprises a threaded eye. In this case, the bore extends into the intermediate section 42 and into the cam disk 20. Although the cam disk 20 is only touched by the eye of the eye circle 52 in the region of the edge 40 facing the bearing section 46, this has the effect that the inner diameters of the bearing section 46, of the intermediate section 44 and of the cam disk 20 are thereby realized, which are identically continuous with respect to these three regions. This facilitates the threading of other shafts or cables.

In fig. 4, an embodiment of the assembly is shown in the assembled state, wherein the drive element 50 with the cam disk 20 corresponds to the drive element 50 of fig. 3 and is not illustrated in detail again. It is furthermore noted that the remaining elements of the transmission are omitted in fig. 4 for greater clarity, for which purpose, as already with regard to fig. 5 and 6, reference is also made to fig. 1 and 2.

The assembly of fig. 4 also comprises a mounting 60, which in the case of fig. 4 is a planet carrier. The planet wheel carrier of fig. 4 has a smaller inner diameter than the drive element 50. However, in this embodiment, a hollow lead-through the planet carrier is also provided.

The mount 60 includes a mount support section 62 having the same outer diameter as the support section 46 of the drive element 50. The mounting support section 62 is defined by a mounting step 63. A fixing is provided by the mounting step 63 and the step 44 of the drive element 50, in which fixing the bearing 64 is accommodated. For the sake of clarity, only the bearing 64 is shown in dashed lines on one side of the sectional view in fig. 4, but is present circumferentially. The inner bearing ring of the bearing 64 is located on the outer circumference of the mounting bearing section 62 and of the bearing section 46 of the drive element 50.

In the embodiment of fig. 4, the mounting support section 62 of the mount 60 is defined by a mating position (Pass-range) slightly smaller than the support section 46 of the drive element 50. The mounting bearing section 62 thereby serves in particular as a centering part, and the bearing section 46 takes over in particular the task of the bearing block. In this way, moreover, a central positioning of the mount 60 relative to the drive element 50 is achieved. The exemplary assembly includes a diaphragm 69 for increasing the coefficient of friction, which is disposed or adapted to fit between the mounting member and the drive member. A typical coefficient of friction of the membrane lies between 0.3 and 0.7, typically between 0.4 and 0.6. The friction fit between the mount 60 and the drive element 50 can be improved by the membrane.

Typical embodiments include a basic deviation of fit on the mounting bearing section which is at least one order of magnitude smaller than the basic deviation of the bearing section of the drive element. The basic deviation is typically related to the diameter of the mounting support section and the support section. Other exemplary embodiments have the same basic deviations at the mounting as at the drive element. Typically, the tolerance levels on the mounting support section and on the support section are the same. In other embodiments, the tolerance levels are different.

In addition, the embodiment of the mount 60 of FIG. 4 includes a mounting hole circle 66 for receiving a coil spring 68. The mounting hole circle 66 has a smaller hole than the hole circle 52 of the drive element 50, but the diameter of the mounting hole circle 66 corresponds to the diameter of the hole circle 52 of the drive element. Furthermore, the holes of the two hole circles 52 and 66 are also matched to one another in that the mounting 60 can be fastened or fixed to the drive element 50 by receiving the bolts 68 in the hole circles 52 and 66 and twisting the bolts 68 into the threads of the holes of the hole circle 52.

Fig. 5 shows a further embodiment of an assembly with a drive element 50 corresponding to the drive element of fig. 3 and a mount 70, wherein the mount 70 is a planet carrier for a hollow shaft preliminary step, wherein the inner diameter of the drive element 50 can be further guided. The inner diameter of the mounting member 70 corresponds to the inner diameter of the drive element, thereby continuously providing the same inner diameter.

In the region of the interface between the drive element 50 and the mounting 70, the embodiment of the assembly of fig. 5 largely corresponds to the embodiment of the assembly of fig. 4, so that the details and features and reference numerals are not explained in depth here, but it is merely to be noted that corresponding reference numerals describe the same or similar features.

Fig. 6 shows a further embodiment of an assembly with a drive element 150 and a mounting 80. The mounting 80 of fig. 6 is configured as a motor shaft which has at least substantially the same inner diameter as the drive element 150.

In general, the mount of typical embodiments has at least substantially the same inner diameter as the drive element. This enables the use of the cross section for threading. Here, "substantially" typically means that the inner diameters deviate from one another by a maximum of 10%, typically by a maximum of 5% or by a maximum of 3%.

The drive element 150 differs from the drive element 50 of the preceding figures in that the contour 22 does not have only two projections but three projections. Thereby, in the cross section of fig. 6, one side at the location with the largest radius is cut (in the lower part of fig. 6) and the location of the contour 22 at the location with the smallest radius contour 22 is cut (in the upper part of fig. 6).

At the location of the smallest radius, the edge 40 on the mounting side transitions at the outer periphery without a step into the middle section 42. This is followed again by the step 44 for clamping the bearing 64.

Partly, in fig. 6, reference numerals have been omitted in the region of the bearing 64, in particular at the mounting, and likewise the hole circle is not provided with reference numerals, for the sake of increased clarity. In this connection, reference is made to the description of fig. 4 and 5, which in connection therewith show similar embodiments. The specificity of the mount 80 of FIG. 6 is also that the mount has an inside diameter that is less than the inside diameter of the drive element 150. This achieves an additional centering step 82, which is located at the inner circumference of the mounting 80 in the region of the interface and acts internally into the inner diameter of the drive element 150.

The present invention is not limited to the embodiments described above, but the scope of the present invention is defined by the contents of the invention described in the specification.

Claims (15)

1. Drive element (50, 150) for a gear mechanism (1) having a plurality of teeth (7) which are guided radially in a tooth carrier (11) and are mounted so as to be movable, said teeth being mounted with their tooth roots on a plurality of pivot segments (24) and with their tooth tips in teeth (5), wherein the drive element (50, 150) comprises:

a cam disk (20) with a contour (22) for mounting a plurality of rolling bodies (23), on which a plurality of pivoting segments (24) are mounted so as to be movable in the circumferential direction,

-a bearing section (46) for receiving a bearing (64), which is arranged axially juxtaposed to the cam disk (20), wherein the bearing section (46) extends in the axial direction such that the entire outer circumference of the bearing section (46) receives the bearing inner ring of the bearing (64),

-a hole circle (52) provided in the support section (46).

2. The drive element (50, 150) according to claim 1, wherein the cam disk (20) is designed hollow, wherein the inner diameter of the cam disk (20) is smaller than the diameter of the hole circle (52).

3. Drive element (50, 150) according to claim 1 or 2, wherein the cam disc (20) comprises an edge (40) for axially supporting the rolling bodies (23).

4. The drive element (50, 150) according to claim 1 or 2, wherein the drive element (50, 150) is of monolithic construction.

5. The drive element (50, 150) according to claim 1 or 2, wherein the drive element (50, 150) is hardened.

6. Drive element (50, 150) according to claim 1 or 2, wherein a step (44) for fixing the bearing is provided between the bearing section (46) and the cam disk (20) at the outer circumference of the drive element (50, 150).

7. The drive element (50, 150) according to claim 1, wherein the transmission (1) is a coaxial transmission.

8. A gear unit having a drive element (50, 150) as claimed in claim 6 and having a plurality of teeth (7) which are guided radially in a tooth carrier (11) and are mounted so as to be movable, said teeth being mounted with their tooth roots on a plurality of pivot segments (24) and with their tooth tips in teeth (5), wherein the pivot segments (24) are mounted with a plurality of rolling bodies (23) on a cam disk of the drive element (50, 150).

9. Assembly with a drive element (50, 150) according to one of claims 1 to 7 and with a mounting (60, 70, 80) which comprises a mounting bearing section (62) with an outer diameter corresponding to the outer diameter of the bearing section (46) of the drive element (50, 150) and/or comprises a mounting hole circle (66) with a diameter corresponding to the diameter of the hole circle (52) of the drive element (50, 150).

10. Assembly according to claim 9, wherein the mounting comprises at the outer periphery a mounting step (63) for fixing a bearing (64), which mounting step is connected to the mounting support section (62).

11. Assembly according to claim 9 or 10, wherein the mounting member (60, 70, 80) is hollow.

12. Assembly according to claim 9 or 10, with a drive device, the driven element (50, 150) of which is connected to the mounting (60, 70, 80) or is embodied in one piece with the mounting (60, 70, 80).

13. Assembly according to claim 9 or 10, with a membrane (69) for increasing the coefficient of friction, which membrane is arranged to be inserted between the mounting member (60, 70, 80) and the drive element (50, 150).

14. A drive train with a transmission (1) according to claim 8 and a drive, the output element (50, 150) of which is connected to the drive element of the transmission (1) by means of a mounting, wherein a bearing inner ring of a bearing is fixed between the mounting step of the mounting and the step of the drive element.

15. Use of a drive element (50, 150) according to any of claims 1 to 7 for connecting a transmission (1) comprising the drive element (50, 150) to a mount.

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