DE102020201460A1 - Planetary gear with hypocycloid guide plate teeth, gear kit and assembly process - Google Patents

Abstract

The proposed solution relates to a planetary gear having a first shaft (S1), a central gear (CG) connected in a rotationally fixed manner to the first shaft (S1), a second shaft (S2), and a planetary web (C) connected in a rotationally fixed manner to the second shaft (S2). , and at least one planetary gear (PG) rotatably mounted on the planetary web (C) and meshing with the central gear (CG), the at least one planetary gear (PG) each having at least one guide element (P). Furthermore, the planetary gear has a guide plate (GP) which is connected to the planetary gear in such a way that at least one of the guide elements (P) engages with a guide plate toothing (GPT) of the guide plate (GP), the course of the guide plate toothing (GPT) is specified on the guide plate (GP) by superimposing hypocycloid trajectories for all guide elements (P) with exactly one number of cycloids (iz). Furthermore, the proposed solution includes a gear kit and an assembly method for providing such a planetary gear.

Description

The proposed solution relates in particular to a planetary gear with a plurality of rotating planetary gears, each of which has at least one guide element which engages with a hypocycloid guide plate toothing, in order to force a superposition of the orbital movement and intrinsic rotation of the planetary gears.

In the course of the advancing automation of actuating mechanisms, for example in the automotive industry, the need for gears for adapting torques and speeds is growing steadily. The relevant transmission parameters are as diverse as the conceivable areas of application, but essentially focus on a differently weighted combination of maximum torque, gear ratio, acoustics and required installation space.

In particular, the comfort-increasing integration of mechatronic actuating drives with gears for the automated execution of setting processes in the immediate vicinity of the user places increased demands on the operating volume of the gears.

If the area of application close to the user also entails additional requirements, such as high torques in the case of a door drive or small installation space in the case of a seat adjustment, conventional gear implementations, especially in single-stage designs, often reach their limits. The limitation of the existing transmission designs not only restricts the degree of design freedom in the design of automated components, but also increases both the assembly effort and the production costs, in particular due to the need for multi-stage systems.

The proposed solution is therefore based on the problem of developing an improved transmission design for the targeted provision of a required speed and torque.

This problem is solved by a planetary gear with the features of claim 1, a gear kit with the features of claim 15 and an assembly method with the features of claim 22.

Such a transmission has at least one first shaft, a central gear connected in a rotationally fixed manner to the first shaft, a planetary web connected in a rotationally fixed manner to a second shaft, a guide plate with guide plate teeth and at least one planetary gear rotatably mounted on the planetary web and meshing with the central gear, the at least each planet gear has at least one guide element which is in engagement with the guide plate teeth.

The course of the guide plate teeth on the guide plate can be described by means of the trajectory of a point which is fixed in relation to a first circle of radius 'r1, the first circle, however, rolling on the inside of a second circle of radius' r2 with r1 <r2. Such a trajectory is referred to as a hypocycloid in the further course of the document and essentially knows three qualitative shapes depending on the spacing s of the point fixed in relation to the first circle from the center point of the first circle.

• - s < r1 ... verkürzte Hypozykloide
• - s = r1 ... gewöhnliche Hypozykloide
• - s > r1 ... verlängerte Hypozykloide.

The following applies here:

• - s <r1 ... shortened hypocycloid
• - s = r1 ... ordinary hypocycloids
• - s> r1 ... elongated hypocycloid.

• - iz < 0 einer gegensinnige Drehung und
• - iz > 0 einer gleichsinnige Drehung

entsprechen.To further characterize the hypocycloid, the number of revolutions of the first circle, based on a complete revolution of the center point of the first circle in the course of the rolling movement in the second circle, can be assigned to it. This number of revolutions is referred to as the cycloid number in the further course of the document iz whose sign indicates the direction of rotation of the first circle in relation to the direction of rotation of the center of the first circle, where:

• - iz <0 an opposite rotation and
• - iz> 0 a rotation in the same direction

are equivalent to.

Thus, a hypocycloid also corresponds to the trajectory of a point that is fixed in relation to the at least one planetary gear when the planetary gear executes a superimposed movement of an orbital movement around a longitudinal axis of the second shaft and a self-rotation around the rotatable connection of the planetary gear with the planetary web.

By supporting the at least one planetary gear with at least one such fixed point on a hypocycloid-shaped guide track, the movement of the at least one planetary gear can thus be restricted to the superimposed orbital movement and intrinsic rotation described above. Basically, it should be noted that the number of guide tracks corresponds to the number of guide elements per planetary gear. The individual guideways are in one plane of the orbital movement of the at least a planet gear by an angular offset α-offset.

For the technical implementation of the hypocycloid-shaped guideways, an inner edge of an internally toothed guide plate can trace the outer edge of the superimposed hypocycloids. Due to the greater curvature of the elongated hypocycloids in the area of the radially outer intersection of the hypocycloid with itself, the outer boundary of the superimposed hypocycloids is longer than the inner boundary of the superimposed hypocycloid. Due to the constant angular speed of the at least one guide element, based on the rotation around the center of the planetary gear, this results in a reduced contact time of the at least one guide element with the inner edge of the superimposed hypocycloids compared to the outer edge of the superimposed hypocycloids. The planet gears are thus supported via the at least one guide element essentially via the outer edge of the superimposed hypocycloid. A further guide plate, which with its external toothing traces the inner edge of the superimposed hypocycloids, can thus be dispensed with in favor of material savings.

In other words, the course of the guide plate toothing on the guide plate is specified by superimposing hypocycloid trajectories for all guide elements with exactly one number of cycloids.

In the case of a drive via the planetary web, the thrust acting on the center point of the at least one planetary gear can consequently be converted proportionally into an inherent rotation of the planetary gear, which can be tapped via the central gear engaged with the planetary gear.

In the case of a drive via the central gear in engagement with the at least one planetary gear, the torque acting on the at least one planetary gear can, on the other hand, be converted proportionally into a thrust acting tangentially on the center of the planetary gear, which sets the planetary web into rotation about the longitudinal axis of the second shaft.

Both in the case of the drive via the planetary web and in the case of the drive via the central wheel, the guide pins describe a sliding rolling movement along the hypocycloid-shaped guide plate toothing. In order to reduce the resistance that occurs here, a rotatably mounted rolling element can be attached to the guide pins under certain circumstances. In a further embodiment variant of the transmission according to the invention that is independent of this, the guide pins can be designed in the shape of a cone or a truncated cone. The guide pins each have an axis of rotation of the cone or truncated cone, said axis of rotation being arranged orthogonally to at least one end face of the at least one planetary gear and a base surface of the cone or truncated cone. In the case of a shaping of the guide pins in which each guide pin has a plurality of orthogonal surfaces with respect to the named axis of rotation, the term base area basically refers to the largest area of the plurality of orthogonal surfaces. Furthermore, the design variants of the guide pins as cones or truncated cones have an opening angle Φ of less than 180 degrees. The opening angle Φ is enclosed by two shortest diametrical connecting lines, which each extend from a point on the edge of the base to the cone tip, in the case of the cones, or the tip constructed by hypothetical extension of the lateral surfaces, in the case of the truncated cones.

In a variant of the conical guide pins, these are also aligned in such a way that the conical base surface is arranged on the side facing away from the planetary gears. An arrangement of the conical base on the side facing the planetary gears is basically also possible. Regardless of the specific shape and arrangement of the guide pins, the guide track can have at least one flat border, which in turn has a shape adapted to the respective shape and arrangement of the guide pins.

Here, the formation of the at least one edge of the guideway is to be understood, for example, as an inclination which has the result that the edge in the gear unit installed as intended is formed such that it can be brought into contact with each of the guide pins along a plurality of contact points. In the specific case of the guide pins being shaped as cones or truncated cones, this means that a section of the shortest connecting sections described above that faces the boundary can be shifted into the boundary of the at least one guideway by parallel displacement, so that the straight line extends completely in the boundary. Such a shaping of the guide pins as a cone or truncated cone with a correspondingly inclined edge of the at least one guide track consequently corresponds to a helical toothing.

By shaping the guide plate teeth as a superposition of hypocycloids, the rotation of the at least one Planet wheel and the rotation of the planet web take place in opposite directions of rotation, that is, with a number of cycloids iz <0.

In particular, the hypocycloids can be shaped as normal hypocycloids in order to minimize the internal resistance of the planetary gear and thus have no points of intersection with themselves. Such a formation can, for example, be a hypocycloid with the number of cycloids iz = -4.

As an alternative, the hypocycloids can be designed as lengthened or shortened hypocycloids for increased expression of an asymmetrical degree of effectiveness. Such formations can, for example, be a hypocycloid with the number of cycloids iz = -1 (shortened) or iz = -6 (extended). Here, an asymmetrical efficiency means in particular that the planetary gear of the solution according to the invention can have self-locking properties.

The course of the guide plate toothing on the guide plate of a planetary gear according to the invention can be predetermined by superimposing common hypocycloidal trajectories for all guide pins in order to realize a drivable web and a drivable central wheel.

Alternatively, the course of the guide plate toothing on the guide plate of a planetary gear according to the invention can be predetermined by superimposing shortened hypocycloid trajectories for all guide pins in order to realize a drivable web and an inhibiting central wheel.

Furthermore, the course of the guide plate toothing on the guide plate of a planetary gear according to the invention can be predetermined by superimposing extended hypocycloidal trajectories for all guide pins in order to realize an inhibiting web and a drivable central wheel.

The toothing of the at least one planet gear with the central wheel can be shaped, for example, in the form of an involute toothing, without being restricted to this shape. Rather, the choice of a specific tooth shape depends on the specific area of application and the associated requirements, such as manufacturing technology, manufacturing costs and durability.

The central gear can be both a sun gear, which meshes with an external toothing of the at least one planetary gear, and a ring gear, which meshes with an internal toothing, the at least one planetary gear.

In the case of an embodiment of the central wheel with an external toothing, a course of the toothing can be predetermined by superimposing cycloid-shaped trajectories for all guide elements with exactly one number of cycloids. The number of cycloids of the central gear teeth can differ from the number of cycloids of the guide plate teeth. In particular, can be cycloid number iz the central gear teeth are really greater than zero and the number of cycloids iz of the guide plate teeth be smaller really smaller zero. In such an embodiment, the central wheel toothing can thus be designed epicycloid-shaped and the guide plate toothing hypocycloid-shaped. In any case, an epicyclic or hypocycloid central gear toothing can be in mesh with at least one of the guide elements of all planetary gears at any time during operation of the planetary gear according to the invention.

In principle, an axis of longitudinal extension of the first shaft can correspond to the longitudinal axis of extension of the second shaft, so that the first and second shafts are arranged coaxially to one another. For this purpose, the guide plate can have a passage for the second shaft.

The end face of the guide plate facing the at least one planet gear lies essentially in one plane. This end face plane of the guide plate can be aligned coplanar to the plane of the planetary web in relation to the face face plane in order to achieve a constant spacing of the at least one planet wheel over the entire circumferential movement of the at least one planet gear. The guide plate can in principle also be designed in one piece with any housing of the planetary gear, into which at least one planetary gear of the proposed solution can be introduced for normal operation.

To support the at least one planetary gear on the guide plate teeth spaced apart from the at least one planetary gear, the at least one planetary gear can have two or more cylindrical guide pins which are firmly connected to the respective planetary gear. The guide pins each have an axis of longitudinal extent which is aligned parallel to the first axis of longitudinal extent of the first shaft. Furthermore, the guide pins are arranged offset radially outward on the respective planetary gear with respect to the rotatable connection of the respective planetary gear with the planetary web.

In the case of a plurality of guide pins, the spacing between the connection point of each guide pin on the associated planetary gear and the rotatable connection of the planetary gear is identical. As a result, all guide pins lie on the outer circumference of a circle with the aforementioned spacing of the guide pins from the planetary gear-planetary web connection, the guide pins further dividing the outer circumference into circular arc segments of equal length.

Depending on the number of cycloids iz the edge of the guide plate toothing of a specific embodiment and a tooth ratio between the number of teeth of the at least one planetary gear and the one central gear, an embodiment of the proposed solution can have an asymmetrical efficiency. This means in particular that the corresponding embodiment can be self-locking with respect to the drive via the central wheel.

In addition, the problem mentioned at the beginning is also solved by a gear kit which has a gear base body which, among other things, has a first shaft, a central gear connected in a rotationally fixed manner to the first shaft, a second shaft, a planetary web connected in a rotationally fixed manner to the second shaft and at least one comprises the planetary web rotatably mounted and the central gear meshing planetary gear with at least one guide element. Furthermore, the gear kit has an interface which is provided for receiving a guide plate selected from a plurality of at least two different guide plates, in such a way that at least one of the guide elements is in engagement with the guide plate toothing. Here, the edges of the guide plate teeth of the at least two different guide plates can be described by superimposing hypocycloid trajectories with the same number of cycloids and all guide elements of all planetary gears.

Basically, the transmission implemented by connecting the basic transmission body to a guide plate as intended corresponds to the initially described planetary transmission of the proposed solution.

The different guide plates of the gear kit can differ, for example, in terms of their number of cycloids, which means that the ratios of the speeds of the planetary web and the central gear during operation of the planetary gear mounted with the gear kit differ depending on the guide plate selected. This allows a modular design of a transmission of the proposed solution for different problem definitions through a targeted selection of a guide plate when using the same basic transmission body.

For the targeted implementation of a gear kit with a wide range of applications, the plurality of differing guide plates can in particular have guide plates, the guide plate teeth of which can be described by superimposing extended, normal and shortened hypocycloidal trajectories of all guide elements of all planetary gears. Thus, the plurality of different guide plates provided for connection to a basic transmission body can be used to implement both a self-locking and a non-self-locking planetary gear.

In addition, the above-mentioned problem is also solved by an assembly method for a gear kit, which, among other things, provides a gear base body with the aforementioned features, selecting a guide plate from a plurality of different guide plates with the aforementioned features and connecting the selected guide plate with having the transmission body.

Here, the planetary gear implemented by carrying out the assembly process as intended corresponds to the initially described planetary gear of the proposed solution.

The attached figures illustrate possible variants of the proposed solution by way of example.

• 1 eine Explosionszeichnung eines Planetengetriebes gemäß der vorgeschlagenen Lösung in einer Ausführung mit drei Planetenrädern, die mit jeweils drei Führungspins entlang einer Führungsplattenverzahnung einer Führungsplatte geführt werden;
• 2 einen Längsschnitt durch ein montiertes Planetengetriebe gemäß der vorgeschlagenen Lösung in einer Ausführung mit drei Planetenrädern;
• 3 einen Querschnitt durch ein Planetengetriebe der vorgeschlagenen Lösung mit Darstellung unterschiedlicher möglicher Trajektorien der Führungspins für die Zykloidzahlen iz ∈ {-1, -2, -3, -4, -5, -6};
• 4 einen Querschnitt durch ein montiertes Planetengetriebe der in 1 und dargestellten Ausführungsform durch die drei Planetenräder;
• 5a einen Querschnitt durch ein montiertes Planetengetriebe der in 1 und dargestellten Ausführungsform durch eine Führungsplatte mit einer Führungsplattenverzahnung entsprechend iz = -4;
• 5b einen Querschnitt durch ein montiertes Planetengetriebe der in 1 und dargestellten Ausführungsform durch eine Führungsplatte mit einer Führungsplattenverzahnung entsprechend iz = -5;
• 5c einen Querschnitt durch ein montiertes Planetengetriebe der in 1 und dargestellten Ausführungsform durch eine Führungsplatte mit einer Führungsplattenverzahnung entsprechend iz = -6;
• 6 einen Querschnitt durch ein montiertes Planetengetriebe der vorgeschlagenen Lösung durch eine äußere Führungsplatte mit einer Führungsplattenverzahnung entsprechend iz = -4 und ein Sonnenrad mit epizykloidförmiger Außenverzahnung entsprechend iz = +3;

Here show:

• 1 an exploded view of a planetary gear according to the proposed solution in an embodiment with three planetary gears, which are each guided with three guide pins along a guide plate toothing of a guide plate;
• 2 a longitudinal section through a mounted planetary gear according to the proposed solution in an embodiment with three planetary gears;
• 3 a cross section through a planetary gear of the proposed solution showing different possible trajectories of the guide pins for the cycloid numbers iz ∈ {-1, -2, -3, -4, -5, -6};
• 4th a cross section through a mounted planetary gear of the in 1 and illustrated embodiment by the three planet gears;
• 5a a cross section through a mounted planetary gear of the in 1 and illustrated embodiment by a guide plate with a guide plate toothing corresponding to iz = -4;
• 5b a cross section through a mounted planetary gear of the in 1 and illustrated embodiment by a guide plate with a guide plate toothing corresponding to iz = -5;
• 5c a cross section through a mounted planetary gear of the in 1 and illustrated embodiment by a guide plate with a guide plate toothing corresponding to iz = -6;
• 6th a cross section through a mounted planetary gear of the proposed solution through an outer guide plate with guide plate teeth corresponding to iz = -4 and a sun gear with epicycloid external teeth corresponding to iz = +3;

1 shows an exploded view of a planetary gear of the proposed solution, having a first shaft S1 , one with the first wave S1 non-rotatably connected central wheel CG , one with a second wave S2 non-rotatably connected planetary web C. , three on the planetary bridge C. rotatably mounted planet gears PG with three guide elements each P. and exactly one guide plate GP with a guide plate toothing GPT , which in the assembled state with at least a subset of the guide elements P. is engaged.

Here is the first wave S1 with a first longitudinal axis AS1 such with the central gear shaped as a sun gear CG rotatably connected that the axis of rotation of the central wheel CG with the first longitudinal axis AS1 coincides. The first wave S1 extends through a circular passage of a planetary gear bearing plate PGBP wherein an inner diameter of the passage is greater than an outer diameter of said first shaft S1 fails. By the illustrated execution of the central wheel CG As an externally toothed sun gear, the component volume can be reduced compared to an equally conceivable design of the central gear CG as an internally toothed ring gear.

In the in 1 The illustrated embodiment of the planetary gear according to the invention is the planetary gear bearing plate PGBP essentially shaped as a hollow circular cylinder, the end faces of which are orthogonal to the first longitudinal axis AS1 are arranged and the aforementioned passage for the first shaft S1 is represented by the inner radius of the hollow cylinder. Furthermore, the planetary gear bearing plate PBGB has a plurality of circular passages that are offset radially outward in relation to the axis of rotation of the hollow cylinder. Here, three of the passages provide rotatable bearings PGB for the three planet gears PG ready, while three more passages for the implementation of one fixation element each FE are provided, which is provided for fixing the mounted planetary gear. As in the embodiment shown, the material thickness of the planetary gear bearing plate can be used PGBP near the passages for the fixation elements FE on the planet gears PG facing away from the face of the planetary gear bearing plate PGBP be reinforced. Such reinforcement FEM can, as in the embodiment variant shown, in one with the planetary gear bearing plate PGBP are firmly connected hollow cylinder, which for this purpose has an inner diameter corresponding to the diameter of the passage. In a further deviation from a shape as an ideal hollow cylinder, the planetary gear bearing plate PGBP beads as shown CO have, which on the one hand reduce the cost of materials and stiffen the planetary gear bearing plate PGBP serve.

The passages for the fixing elements are distributed here FE on an outer boundary of a circle, the center of which coincides with the first longitudinal axis AS1 coincides in such a way that the passages for the fixing elements FE Divide the edge of the circle into arc segments of equal length. The same applies to the three passages for the rotatable mounting PGB of the planetary gears PG with a possibly different circle radius.

The central wheel CG points to its the first wave S1 facing away from the end face a pin shaped as a cylinder CGB on, being the axis of rotation of the cylinder CGB with the first longitudinal axis AS1 coincides. This cone CGB extends into the central opening of the planetary web, which is designed as a hollow circular cylinder C. . Due to the storage of the first wave S1 with a central tenon CGB in the planetary bridge C. the smoothness and thus the acoustics of the transmission can be improved. In addition, the load limit improves with regard to a maximum non-destructive translatable torque. In principle, however, the first shaft can also be cantilevered S1 conceivable, especially if the smoothness and service life are of secondary importance, or the torques that occur turn out to be low.

The second wave S2 is non-rotatable with the planetary bridge C. connected. The two end faces of the hollow circular cylinder are orthogonal to the first longitudinal axis AS1 aligned and the second wave S2 connected to the hollow circular cylinder in such a way that a second longitudinal axis AS2 the second wave S2 and the axis of rotation of the hollow circular cylinder coincide. Consequently, the first and second longitudinal axes also fall AS1 , AS2 together, with which a coaxial gear arrangement is realized. Basically, an eccentric mounting of the second shaft is also involved S2 , or a connection of the planetary bridge C. with the second wave S2 conceivable via a crankshaft.

The extension length of the hollow circular cylinder along its axis of rotation can be smaller, in particular smaller than a tenth of the diameter of the base area of the hollow circular cylinder, to reduce the cost of material, as in the case shown. A lower limit of the extension length of the hollow circular cylinder along its axis of rotation can be determined by means of the maximum acting torques known for a specific application. In contrast, a lower limit of the diameter of the hollow circular cylinder is given by the sum of the radii of the planetary gear PG and the central wheel CG and can thus be designed from the point of view of a targeted central gear-planetary gear set.

Furthermore, the in 1 illustrated planet bar C. one of the number of planet gears PG Corresponding number of passages for the rotatable mounting of the planetary gears PG on. The passages for mounting the planetary gears are distributed here PG on an outer edge of a circle with one with the first longitudinal axis AS1 coinciding center, whereby the outer edge of the passages is divided into circular arc segments of equal length.

This corresponds to the relative to the first longitudinal axis AS1 radial distance between the centers of the passages for mounting the planetary gears PG on the planetary gear bearing plate PGBP the radial distance between the centers of the passages for mounting the planetary gears PG on the planetary bridge C. .

Each of the three planet gears PG is consequently with the respective axis of rotation parallel to the first axis of longitudinal extension AS1 aligned. There is also a number of planet gears that differs from three PG possible as long as the planetary gears PG are sufficiently spaced from one another so as not to come into direct contact with one another. All planet gears PG each point on their the planetary gear bearing plate PGBP facing end face a pin shaped as a cylinder PGB on, which is for rotatable mounting in the passages for the rotatable mounting of the planetary gears PG in the planetary bearing plate PGBP extends. Furthermore, the planet gears PG each on their the planetary gear bearing plate PGBP facing away from the end face three guide elements designed in the form of a cylinder P. on, which is parallel to the axis of rotation of the respective planetary gear PG are arranged.

The guiding elements P. lie on an outer edge of a circle with one with the axis of rotation of the respective planetary gear PG coinciding center point, the outer edge of the guide elements P. is divided into circular arc segments of equal length. There are the planetary gears PG designed and arranged such that each of the three planetary gears contained in this embodiment PG the one with the first wave S1 connected central wheel CG combs.

In the in 1 The illustrated embodiment extend the planet gears PG with a cylindrical section through the passages for the rotatable mounting of the planetary gears PG in the planetary bridge C. . The guide elements thus protrude P. of the planetary gears PG about the planet gears PG remote face of the planetary web C. out and grip the guide plate teeth there GPT the guide plate GP .

The guide plate GP is here essentially as an internally toothed central gear CG designed, the boundary of the internal toothing by a superposition of three hypocycloid-shaped and an angular offset α of 120 ° to each other about the first longitudinal axis AS1 rotated trajectories of a cycloid number iz from -4 is writable.

The angular offset is aligned here α of the trajectories according to the number NP of the guide elements P. per planetary gear PG , such that $$\alpha =360°/N\mathrm{P.}.$$

Basically, it should be noted that the number of cam tracks in the guide plate GP the number NP of the guide elements P. per planetary gear PG is equivalent to. Thus requires a certain number NP on guide elements P. an equally large number of trajectories, thereby increasing the number NP of the guide elements P. with a reduction in the rigidity of the guide plate teeth GPT can go hand in hand.

In the in 1 illustrated embodiment, the planetary gear according to the invention has a housing H on, which essentially consists of an annular end face HF and a jacket surface connected to it, corresponding to the jacket of a circular cylinder HS is formed. The outside diameter corresponds to the face HF the diameter of the outer surface HS . Furthermore, the jacket surface HS Lanyard HL1 to connect the housing H via lanyards HL2 the guide plate GP with the guide plate GP have, said connecting means HL1 , HL2 A form-fitting or force-fitting connection of the housing that may be detachable under certain circumstances may be suitable H with the guide plate GP to manufacture.

Thus, in the properly installed state, the illustrated embodiment of the proposed solution encloses the one with the guide plate GP connected housing H the planetary bridge C. without being in force or frictional contact with it. casing H and guide plate GP consequently close a transmission interior IS on.

In addition, alternative and equivalent embodiments of the proposed solution are possible. Here, for example, the planetary web C. be designed in a shape deviating from a circular cylinder, wherein the shape of the circular cylinder can be characterized by reduced manufacturing costs and / or increased load capacity. Other conceivable shapes of the planetary web C. include, for example, a star-shaped formation, consisting of three essentially linearly extending radial elements, each with one end on the second shaft S2 are attached, each two adjacent radial elements enclose an angle of approximately 120 °. Thus, they form with the second wave S2 connected radial elements essentially the interior angle bisector of an equilateral triangle, the corner points each having a rotatable bearing PGB of a planet gear PG can provide.

Such a star-shaped design can be readily applied to embodiments of the proposed solution with one of the number of planet gears shown PG adapt to different number. Regardless of the number of planet gears PG is reduced by using a star-shaped planetary bridge C. compared to the embodiment as a circular cylinder, the cost of material and thus also the moment of inertia.

In principle, a larger number of guide elements can also be used P. than in 1 shown with each planet gear PG be connected as long as the number NP of the guide elements P. per planetary gear PG fails the same. There can be an increased number NP on guide elements P. a load on the individual guide elements P. as well as the edge of the guide plate teeth GPT against which the guide elements P. support, reduce. In any case, there should be a plurality of guide elements P. of each planet gear PG be arranged such that the guide elements P. on an outer circumference of a circle with for all planet gears PG same diameter around the rotatable bearing PGB of the respective planet gear PG come to rest. Furthermore, the majority of guide elements should P. of each planet gear PG , divide the said circle into circular arc segments of equal length.

Here, the guide elements P. rotatable on the planetary gears PG be stored or in an alternative embodiment also via a one-piece design or compression with the respective planetary gear PG be firmly connected. In this case, the guide elements P. a rotatably mounted roller body can be attached to material removal and friction loss values when moving along the guide plate toothing GPT to improve. Furthermore, the guide pins can in principle have a shape that differs from a cylinder. Such a deviation can exist, for example, in the conical or frustoconical shape described at the beginning. However, guide pins with an edgeless surface are also conceivable, an edgeless surface representing a continuously differentiable two-dimensional manifold.

In the present case (cf. 1 ) it concerns the toothing of the planetary gears PG an involute toothing. In principle, however, other tooth shapes are also conceivable, as long as they match the toothing of the central wheel CG to get voted.

In a variant that differs from the embodiment shown, the guide plate GP basically have a portion which is the rotatable bearing of the first or second shaft S1 , S2 serves. Such a section can, for example, be based on the longitudinal extension axis of the respective shaft S1 , S2 be centrally arranged pin, which is designed as a hollow shaft with the respective shaft S1 , S2 is engaged.

In addition, the guide plate PG can also be arranged in positions that differ from the illustration. Based on the 1 The arrangement shown is therefore basically also an arrangement between the planetary gears PG and the planetary gear bearing plate PGBP as well as between the planetary gear bearing plate PGBP and the housing face HF conceivable. From the use of a planetary gear bearing plate PGBP can also be waived entirely.

Here, the guide plate GP in any of the possible arrangements with the housing H be made in one piece. A housing that completely encloses the planetary gear can also be used H are used, which thus only one passage for the first and second shaft S2 having, with regard to the assembly of the housing H this could be separated or inseparably joined together from several housing elements. For such a solution according to the invention with a housing that completely encloses the planetary gear H , would be the interior of the gearbox IS only through the inside of the housing H be limited. In any case, the interior of the gear unit is shielded IS of all variants according to the invention, among other things, to accommodate the central wheel CG and the planetary gear PG intended.

In principle, however, it should be noted that the arrangement of the guide plate shown here GP the possibility of modular use of the transmission is improved, since the guide plate according to the invention is replaced GP no further components of the planetary gear have to be dismantled.

In a further variant of the solution according to the invention, the openings in the interior of the transmission can IS , in which two elements moving relative to one another are opposite, are also shielded against the ingress of smaller particles and / or liquids by the use of sealing elements.

2 shows a longitudinal section of an inventive planetary gear corresponding to that in 1 illustrated embodiment, wherein the sectional plane through a relative to the first longitudinal axis AS1 perpendicular, through a planetary gear PG extending radial beam and the first longitudinal axis AS1 is formed.

In the embodiment shown, the first shaft, designed as a hollow shaft, extends S1 through a passage in the planetary bearing plate PGBP . The passage is created here by the inner diameter of the planetary bearing plate, which is essentially shaped as a hollow circular cylinder PGBP provided, the end faces of which are orthogonal to the first longitudinal axis AS1 are arranged. Here, the planetary bearing plate PGBP along its inner diameter on a material collar with which the planetary bearing plate PGBP against a passage on the front side HF of the housing H supports.

The longitudinal section also shows the planetary gear bearing plate PGBP two passages offset radially outward relative to the axis of rotation of the hollow cylinder. Here, one of the passages provides a rotatable bearing for one of the three planetary gears PG ready, while the further passage for the implementation of a fixation element FE is provided, which is used to fix the mounted planetary gear. As in the embodiment shown, the material thickness of the planetary gear bearing plate can be used PGBP near the passages for the fixation elements FE on the planet gears PG facing away from the face of the planetary gear bearing plate PGBP be reinforced. Such reinforcement FEM can, as in the embodiment variant shown, in one with the planetary gear bearing plate PGBP are firmly connected hollow cylinder, which for this purpose has an inner diameter corresponding to the diameter of the passage. This gives way to the shape of the planetary gear bearing plate PGBP depends on an ideal hollow circular cylinder. Furthermore, the planetary gear bearing plate PGBP Beads CO have in which projections of the planetary web C. can intervene positively.

Furthermore is the first wave S1 with the central gear designed as a sun gear CG connected, which on its the first wave S1 facing away from the end face a pin shaped as a cylinder CGB having. This cone CGB extends into a bearing for the first shaft S1 provided central opening of the planetary web C. , which is essentially designed as a hollow circular cylinder for this purpose. Due to the storage of the first wave S1 with the central tenon CGB in the central passage of the planet bar shaped as a hollow circular cylinder C. the smoothness and thus the acoustics of the transmission can be improved. In addition, the load limit improves with regard to a maximum non-destructive translatable torque.

Furthermore is the second wave S2 non-rotatably with the planetary bridge C. connected, the axis of rotation of the planetary web C. and the second longitudinal extension axis AS2 coincide. Furthermore, the in 1 illustrated planet bar C. a passage for the rotatable mounting of the one illustrated planet gear PG . This corresponds to the relative to the first longitudinal axis AS1 radial distance between the centers of the passages for mounting the planetary gears PG on the planetary gear bearing plate PGBP the radial distance between the centers of the passages for mounting the planetary gears PG on the planetary bridge C. .

Thus, the one shown is a planetary gear PG with the axis of rotation parallel to the first axis of longitudinal extension AS1 aligned. The planet gear shown PG has its the planetary gear bearing plate PGBP facing end face the pin shaped as a cylinder PGB on, which is for rotatable mounting in the Passages for the rotatable mounting of the planetary gears PG extends in the planetary bearing plate. In addition, it shows a planet gear shown PG on its the planetary gear bearing plate PGBP facing away from the end face a plurality of guide elements in the form of a cylinder P. which is parallel to the axis of rotation of the planetary gear PG are arranged.

In the in 2 illustrated embodiment, the planetary gear according to the invention has a housing H on, which essentially consists of an annular end face HF and a jacket surface connected to it, corresponding to the jacket of a circular cylinder HS is formed. The outside diameter corresponds to the face HF the diameter of the outer surface HS . In the variant shown here, the housing is H also with the guide plate GP connected in a manner not shown in order to create a transmission interior IS shield at least essentially.

3 shows a cross section along one through the planet gears PG running and based on the first longitudinal axis AS1 orthogonal sectional plane of the planetary gear installed according to the invention of the representations 1 and 2 with three planet gears PG and one the three planet gears PG meshing sun gear CG .

The rotatably mounted externally toothed planetary gears PG In the embodiment shown, each have three bearings for three cylindrical guide elements P. on, which with a guide plate toothing GPT a guide plate GP can be engaged.

With a drive via the sun gear CG acts on every planet gear PG a torque. Due to the forced guidance of the guide elements P. in the hypocycloid-shaped guide plate toothing GPT becomes the counter-rotating self-rotation of the planet gears PG in a tangential to the illustrated trajectory of the planetary gear center PGCT directed thrust transferred.

As each of the three planet gears PG the in 3 embodiment shown rotatable along the respective axis of rotation with the planetary web, not shown C. connected, results from the revolution of the planet gears PG one related to the natural rotation of the planetary gears PG opposite rotation of the planet bar C. . Via the non-rotatable connection of the planetary bar C. with the second wave S2 the increased or reduced speed can thus be tapped.

The ones from the guiding elements P. The trajectories described in the course of the orbital movement with superimposed rotation are for different numbers of cycloids iz shown. Here each of the three planet gears takes place PG one of the cycloid number iz corresponding number of rotations around the respective planetary gear center point, while the respective planetary gear center point once around the second longitudinal axis AS2 running around.

For the embodiment shown here, the hypocycloids describe the number of cycloids iz -1, -2 and -3 shortened hypocycloids, the hypocycloids of the cycloid number iz -4 an ordinary hypocycloid and the hypocycloids of the cycloid numbers iz less than or equal to -5 elongated hypocycloids.

4th shows a cross section along one through the planet gears PG running and based on the first longitudinal axis AS1 orthogonal sectional plane of the planetary gear installed according to the invention of the representations 1 until 3 with three planet gears PG . In addition to those in the 3 transmission elements shown, shows the 4th here the planetary bearing plate with three passages for the fixing elements FE , as well as three essentially triangular beads CO .

5a shows a further cross section along a through the guide plate GP running and based on the first longitudinal axis AS1 orthogonal sectional plane of the planetary gear installed according to the invention of the representations 1 until 3 , with representation of the plane of the planet gears lying outside the cutting plane PG . The three guide elements each extend here P. of the three planet gears PG orthogonal to the plane of the figure and thus project at least partially in the plane of the guide plate GP . At least one of the plurality of guide elements engages there P. per planetary gear PG into the guide plate teeth GPT the guide plate GP . In the operating state of the mounted planetary gear shown, there is one guide element in each case P. of the three planet gears PG with the guide plate teeth GPT the number of cycloids iz = -4 engaged.

5b shows one of the 5a corresponding illustration with a different guide plate GP the number of cycloids iz = -5, which according to the transmission kit according to the invention with the in the 5a transmission body shown is connectable.

5c shows one of the 5a corresponding illustration with a different guide plate GP the number of cycloids iz = -6, which according to the transmission kit according to the invention with the in the 5a and 5b transmission body shown is connectable.

6th shows a cross section along a through the guide plate GP running and based on the first longitudinal axis AS1 orthogonal sectional plane of the planetary gear installed according to the invention in a further variant with three planetary gears PG without external teeth and one of the three planet gears PG meshing sun gear CG with an epicycloid-shaped toothing of the number of cycloids iz = +3.

The rotatably mounted planetary gears PG without external toothing, in the embodiment shown, each have three cylindrical guide elements P. on which both the guide plate teeth GPT the guide plate GP as well as with the sun gear CG are engaged.

With a drive via the sun gear CG acts on every planet gear PG a torque. Due to the forced guidance of the guide elements P. in the hypocycloid-shaped guide plate toothing GPT becomes the counter-rotating self-rotation of the planet gears PG in a tangential to the illustrated trajectory of the planetary gear center PGCT directed thrust transferred.

As each of the three planet gears PG the in 6th embodiment shown rotatable along the respective axis of rotation with the planetary web, not shown C. connected, results from the revolution of the planet gears PG one related to the natural rotation of the planetary gears PG opposite rotation of the planet bar C. . Via the non-rotatable connection of the planetary bar C. with the second wave S2 the increased or reduced speed can thus be tapped.

List of reference symbols

S1

first wave

AS1

first longitudinal axis

S2

second wave

S2B

rotatable mounting of the second shaft

AS2

second longitudinal axis

C.

Planetary bridge

PG

Planetary gear

PGB

rotatable planetary gear bearing

PGT

Planetary gear teeth

PGCT

Trajectory of the center of the planet gear

PGBP

Planetary gear bearing plate

CO

Beads

P.

Guide element

NP

Number of guide pins per planetary gear

PB

Storage of the guide pin

iz

Cycloid number

α-

Angular misalignment of the guideway

GP

Guide plate

GPT

Guide plate teeth

IS

Transmission interior

CG

Central wheel

CGB

rotating central wheel bearing

CGT

Central gear teeth

FE

Fixation element

FEM

Receiving section for the fixing element

H

Planetary gear housing

HS

Outer surface of the planetary gear housing

HF

Face of the planetary gear housing

HL1

Lanyard

HL2

Lanyard

Claims (25)

Planetary gear, comprising: - a first shaft (S1), - a central wheel (CG) connected in a rotationally fixed manner to the first shaft (S1), - a second shaft (S2), - a planetary web (C ), - At least one planetary gear (PG) rotatably mounted on the planetary web (C) and meshing with the central gear (CG), the at least one planetary gear (PG) each having at least one guide element (P), characterized in that the Planetary gear furthermore has a guide plate (GP) which is connected to the planetary gear in such a way that at least one of the guide elements (P) engages with a guide plate toothing (GPT) of the guide plate (GP), the course of the guide plate toothing (GPT) on the Guide plate (GP) is given by an overlay of hypocycloid trajectories for all guide elements (P) with exactly one number of cycloids (iz). Planetary gear according to Claim 1 , characterized in that the guide plate toothing (GPT) for driving the planetary web (C) converts a drive on the central wheel side into a superimposition of an orbital movement of the at least one planet wheel (PG) and a natural rotation of the at least one planet wheel (PG). Planetary gear according to Claim 2 , characterized in that the guide elements (P) are designed as cylindrical guide pins. Planetary gear according to Claim 3 , characterized in that the guide pins (P) convert the thrust on the central wheel side into an orbital movement of the at least one planet wheel (PG) around the second shaft (S2) by means of a combined sliding and rolling movement. Planetary gear according to Claim 4 , characterized in that the course of the guide plate toothing (GPT) on the guide plate (GP) is specified by superimposing normal or shortened hypocycloid trajectories for all guide pins (P) to increase the sliding component in the combined sliding-rolling movement of the guide pins (P) . Planetary gear according to Claim 4 , characterized in that, in order to reduce the sliding component in the combined sliding-rolling movement of the guide pins (P), the course of the guide plate toothing (GPT) on the guide plate (GP) is predetermined by superimposing extended hypocycloid trajectories for all guide pins (P). Planetary gear according to Claim 6 , characterized in that the planetary gear is self-locking. Planetary gear according to one of the Claims 3 until 7th , characterized in that at least one rolling element can be arranged on the guide pins (P) in order to minimize the resistance. Planetary gear according to one of the preceding claims, characterized in that the guide plate (GP) can be connected to a housing (H) of the planetary gear in such a way that the housing (H) connected to the guide plate (GP) encloses a gear interior (IS) which for this purpose it is provided to accommodate the at least one planet gear and the central gear. Planetary gear according to one of the preceding claims, characterized in that the central gear (CG) has internal teeth (CGT) with which the central gear (CG) meshes with the at least one planetary gear (PG). Planetary gear according to one of the Claims 1 until 9 , characterized in that the central gear (CG) has external teeth (CGT) with which the central gear (CG) meshes with the at least one planetary gear (PG). Planetary gear according to Claim 11 , characterized in that the central wheel (CG) has a cycloid toothing (CGT), the course of the cycloid toothing (CGT) being predetermined by superimposing cycloid trajectories for all guide elements (P) with exactly one number of cycloids (iz). Planetary gear according to one of the preceding claims, characterized in that the central wheel (CG) meshes with the guide elements (P). Planetary gear according to one of the preceding claims, characterized in that the planetary gear has a planetary bearing plate (PGBP) which has at least one of the number of planetary gears (PG) corresponding number of passages for mounting the planetary gears (PG). Gearbox kit comprising: - a gearbox base body, comprising: o a first shaft (S1), o a central wheel (CG) connected in a rotationally fixed manner to the first shaft (S1), o a second shaft (S2), o one to the second shaft (S2) non-rotatably connected planetary web (C), o at least one planetary gear (PG) rotatably mounted on the planetary web (C) and meshing with the central gear (CG), the at least one planetary gear (PG) each having at least one guide element (P), characterized in that the basic transmission body also has an interface for receiving a guide plate (GP), the course of the guide plate toothing (GPT) on the guide plate (GP) by superimposing hypocycloid trajectories for all guide elements (P) with exactly one number of cycloids (iz ) is specified, and - optionally one of at least two different guide plates (GP) can be connected to the basic transmission body, and - each of the at least two guide plates ten (GP) can be received by the interface in such a way that at least one of the guide elements (P) is in engagement with the guide plate toothing (GPT) of the guide plate (GP). Gear kit according to Claim 15 , characterized in that the at least two different guide plates (GP) differ with regard to the number of cycloids (iz) of the hypocycloid trajectories that determine the course of the guide plate toothing (GPT). Gear kit according to Claim 15 or 16 , characterized in that the course of the guide plate toothing (GPT) on the guide plate (GP) is predetermined by superimposing extended hypocycloid trajectories for all guide pins (P). Gear kit according to Claim 15 or 16 , characterized in that the course of the guide plate toothing (GPT) on the guide plate (GP) is predetermined by superimposing shortened or normal hypocycloidal trajectories for all guide pins (P). Gear kit according to one of the Claims 15 until 18th , characterized in that the central wheel (CG) has a cycloid toothing (CGT), the course of the cycloid toothing (CGT) being predetermined by superimposing cycloid trajectories for all guide elements (P) with exactly one number of cycloids (iz). Gear kit according to one of the Claims 15 until 19th , characterized in that the central wheel (CG) meshes with the guide elements (P). Gear kit according to one of the Claims 15 until 20th , characterized in that the gear kit has a planetary bearing plate (PGBP) which has at least one of the number of planetary gears (PG) corresponding number of passages for mounting the planetary gears (PG). Assembly method for a gear kit, comprising: providing a gear basic body which: o a first shaft (S1), o a central wheel (CG) connected non-rotatably to the first shaft (S1), o a second shaft (S2), o one with the second shaft (S2) non-rotatably connected planetary web (C), o at least one planetary gear (PG) rotatably mounted on the planetary web (C) and meshing with the central gear (CG), the at least one planetary gear (PG) each having at least one Has guide element (P), and characterized in that the basic transmission body also has an interface for receiving a guide plate (GP), the course of the guide plate toothing (GPT) on the guide plate (GP) by superimposing hypocycloid trajectories for all guide elements (P ) is specified for exactly one number of cycloids (iz), and the assembly method further comprises: selecting one of at least two different guide plates en (GP), as well as - a connection of the selected guide plate (GP) via the interface with the transmission base body, the selected guide plate (GP) being received by the interface in such a way that at least one of the guide elements (P) with the guide plate toothing (GPT) the guide plate (GP) is engaged. Assembly method according to Claim 22 , characterized in that a ratio of the speeds of the planetary web (C) and the central wheel (CG) can be set by selecting one of several different guide plates (GP) during operation of the planetary gear installed with the gear kit. Assembly method according to one of the Claims 22 and 23 , characterized in that the central wheel (CG) of the gear kit provided has a cycloid toothing (CGT), the course of the cycloid toothing (CGT) being given by superimposing cycloid trajectories for all guide elements (P) with exactly one number of cycloids (iz) is. Assembly method according to one of the Claims 22 until 24 , characterized in that the central wheel (CG) meshes with the guide elements (P).

Images