DE102013201520A1 - Circulation gear-transmission for electromechanical actuator utilized for e.g. motor car, has input part and output part, planetary gears provided between wheels and ring gears, where ring gears are supported independent of bearing - Google Patents

Abstract

The gear-transmission (1) has an input part (2) and an output part (3), and ring gears (15-17) arranged between two translation stages (I, II, III). An electromechanical actuator incorporates components. Planetary gears (26, 29, 30) are provided between sun wheels (6, 22, 23) and ring gears. The ring gears are supported independent of a bearing (25). The sun wheels are supported on bolts (5, 19). Planet carriers (24, 27) are radially outside of the bearing of the sun wheel. The input part is connected with a rotor shaft (4) of an electromotor.

Description

Field of the invention

The invention relates to an epicyclic gearbox, in particular for an electromechanical actuator having an input part and an output part and having at least two arranged between these translation stages, containing the components at least one ring gear, each one associated with a gear ratio sun gear and each associated with a gear ratio planet carrier with distributed over the circumference , planetary gears meshing between sun gear and ring gear.

Background of the invention

Planetary gear, for example in the form of arranged between two shafts, a translation into fast or slow between the two shafts planetary gears providing are well known. Here, a plurality of gear ratios with a ring gear, a sun gear and meshing therebetween, distributed over the circumference and rotatably received on a planet carrier planetary gears be connected in series. In less demanding applications, individual gear ratios of multi-stage epicyclic gears, for example for electromechanical actuators, for example for roll stabilizers, lane and / or camber adjustments and the like can be provided without their own bearings. Both the centering and the leadership of the entire transmission network and the individual gear stages takes place via a head clearance between the sun gear, the associated planetary gears and the associated ring gear. Here, a ring gear for individual groups or all gear stages to minimize the number of parts and from aspects of assembly, manufacturing and cost reasons can be formed directly as a continuous teeth in the housing of an electromechanical actuator.

Furthermore, for example, from the DE 10 2009 006 385 A1 an electromechanical actuator with a planetary gear and a switched-torsion with an elastomer decoupling known. On the one hand, the object of this torsion element is to allow small angles of rotation of the actuator without exerting a negative influence on the actuator drive. On the other hand, the drive unit is protected against overload by the elasticity of the torsion element when high dynamic forces are applied. As a result of the function-related and necessary to fulfill the function of such a torsional elasticity element, there may be in the transmission during operation to Deaxierungen, to tilts of each gear stages to each other and high axial and radial reaction forces. Possible consequences include undefined tooth interventions and resulting unclear or unknown balance of power within the transmission network. As a result of the tilting and disabling of individual gear stages which is favored as a result, it is possible for gear stages to wobble which, in addition to a non-round overall run with undefined behavior, can also lead to a sharp increase in friction within the gearbox. This can be associated with a significant drop in transmission efficiency. As further consequences, a significantly increased wear and a shortened life can occur. To reduce or completely prevent these effects, the storage of each gear stage in the form of a fixed-floating bearing can be designed by two separate bearings in a known manner, which are supported radially relative to a housing of the actuator. However, since it requires six bearings for complete storage in an example three-stage planetary gear, brings a design of the storage, each with a bearing on the drive and output side of each gear stage a relatively high demand for axial space with it. However, this axial space is often not available for electromechanical actuators, especially for roll stabilizers. Another disadvantage of such a conventionally mounted design is that all bearings of the individual gear stages need a radial support relative to the actuator housing. This means that specific components are required between the individual stages of the transmission to ensure the coaxiality and thus the functionality of the bearings. However, such a housing-supported arrangement is in clear contradiction to the design of the ring gear as a continuous for all gear stages contour in the housing.

Object of the invention

The object of the invention is the development of a planetary gear with improved storage concept.

General description of the invention

The object is solved by the subject matter of claim 1, which depend on claim 1 dependent claims give advantageous embodiments again.

The proposed epicyclic gearing is particularly suitable for an electromechanical actuator, for example in a roll stabilizer, a lane and / or lintel and the like is provided in a motor vehicle. The epicyclic gearbox has an input part and an output part and at least two arranged between these gear ratios with each of the components ring gear, sun gear and planet carrier distributed over the circumference, meshing between the sun and ring gear planetary gears. The ring gears of individual or all gear ratios can be formed in one piece. Advantageously, at least two components, preferably sun gears and / or planet carriers by means of radially and / or axially overlapping bearings on each other and stored independently of a storage relative to the at least one ring gear. This means that none of the components sun gear and planet carrier is mounted via gears of the ring gear or within the teeth of the individual ring gears.

In an advantageous manner, at least two components can be mounted directly or indirectly on the input side and / or output side on a bolt arranged radially inwards. Advantageously, all sun gears can be mounted on bolts and at least two sun gears on different bolts. Under bolts here shaft and axle sections can be understood.

In an advantageous embodiment, a torsion element with two mutually limited against the action of an effective energy storage device in the circumferential direction rotatable components is arranged between the input part or output part and subsequent translation stage. In this case, one of these components can receive a planet carrier this translation stage and be provided between the components an axial and radial bearing.

In an advantageous electromechanical actuator with the proposed epicyclic gearing, an input part of the epicyclic gearbox may be rotationally connected to a rotor shaft of an electric motor, and the planet carrier of the gear stage connected to the rotor shaft by means of the sun gear may be rotatably mounted on a housing of the electric motor. Alternatively, an input part of the epicyclic gearbox can be rotationally connected to a rotor shaft of an electric motor and the planet carrier can be rotatably mounted on the rotor shaft via the gear stage connected to the rotor by means of the sun gear.

A nested formation of bearings can be provided by two planetary carrier axially adjacent translation stages are mounted rotatably on each other. In this case, a bearing point of the two planet carriers can be arranged radially outside of a bearing point of the sun gear of one of the transmission stages on the bolt.

The types of bearings, such as rolling and / or plain bearings, can be specified freely. However, it may be provided to arrange between the sun gears and the pin plain bearings and between the components of the gear ratios rolling bearings, in particular fixed bearings.

• – Vollständige Lagerung sämtlicher Übersetzungsstufen des Umlaufrädergetriebes sowohl an ihrer Abtriebs- als auch an ihrer Antriebsseite;
• – Ausführung sämtlicher Lagerstellen bevorzugt als ineinander geschachtelte Lagerstellen, um mehrere Lagerstellen in möglichst wenig axialen Bauraum zu integrieren;
• – Ausführung dieser einzelnen Lagerstellen in der Art, dass eine Abstützung der Lagerstellen nach außen, beispielsweise an einem Gehäuse des elektromechanischen Wankstabilisators nicht erforderlich ist und somit die Hohlräder des Umlaufrädergetriebes als eine für alle Übersetzungsstufen durchgängige und voll in ein Aktuatorgehäuse integrierte Verzahnung ausgestaltet werden können;
• – Ausführung dieser einzelnen Lagerstellen in der Art, dass eine Abstützung sämtlicher Lagerstellen über einen oder mehrere zentral in einem Getriebeverbund des Umlaufrädergetriebes liegende und an Antriebs- oder Abtriebsseite angebundene Bolzen erfolgen kann;
• – Einsatz eines Torsionselements mit einer gegenüber einer Außenkontur entgegen der Wirkung eines in Umfangsrichtung wirksamen Energiespeichers wie zumindest einer oder mehrerer Gummi- und/oder Stahlfedern (siehe hierzu DE 10 2009 006 385 A1 ) zur Dämpfung und Entkopplung der Abtriebsseite von einer der Antriebseinheit, welches zugleich als Planetenträger der dritten Übersetzungsstufe dienen kann. Hierbei kann dessen äußeres Gehäuse beziehungsweise dessen Außenkontur über einen direkt angeformten konzentrischen Bund sowohl die axiale als auch die radiale Lagerung der Innenkontur des Torsionselements sicherstellen und damit als einzigen verbleibenden Freiheitsgrad die Verdrehung der Innen- zur Außenkontur zulassen. Insbesondere können folgende vorteilhafte Ausführungsformen vorgesehen sein:
• – Lagerung des Sonnenrads der zweiten Übersetzungsstufe auf einem Bolzen, welcher direkt an der Innenkontur des Torsionselements befestigt ist oder dort direkt angeformt ist;
• – Lagerung des Sonnenrads der dritten Stufe auf einem Bolzen, welcher direkt an der Innenkontur des Torsionselements befestigt ist oder dort direkt angeformt ist.
• – Lagerung des Planetenträgers der ersten Übersetzungsstufe antriebsseitig entweder nach innen auf einem mit einer Rotorwelle des Elektromotors gemeinsam drehenden oder aus dieser gebildeten Bolzen oder radial außen an einem Gehäuse des Elektromotors;
• – Lagerung des Planetenträgers der zweiten Übersetzungsstufe antriebsseitig über eine Lagerstelle, die sich an der Lagerstelle des zugehörigen Sonnenrads der zweiten Übersetzungsstufe abstützt, das seinerseits wiederum drehbar auf dem zuvor bereits beschriebenen, der Innenkontur des Torsionselement zugeordneten Bolzen gelagert ist;
• – Entsprechend kann das beschriebene dreistufige Umlaufrädergetriebe zweioder mehr als dreistufig ausgebildet sein.

The proposed planetary gear transmission - described here for three gear ratios -, an electromechanical actuator with this and in particular a roll stabilization have, for example, the following advantages and forms of training:

• - Complete storage of all gear ratios of the epicyclic gearbox on both its output and on its drive side;
• - Execution of all bearings preferred as nested bearings, to integrate multiple bearings in the least possible axial space;
• - Execution of these individual bearings in the way that a support of the bearings to the outside, for example, on a housing of the electromechanical roll stabilizer is not required and thus the ring gears of the planetary gear can be configured as one integrated for all gear ratios and fully integrated into an actuator housing gearing;
• - Execution of these individual bearings in the way that a support of all bearings can be done via one or more centrally located in a transmission network of Umlaufrädergetriebes and connected to the drive or driven side bolt;
• - Use of a torsion element with respect to an outer contour against the action of a circumferentially effective energy storage as at least one or more rubber and / or steel springs (see DE 10 2009 006 385 A1 ) for damping and decoupling the output side of one of the drive unit, which can serve as a planet carrier of the third gear stage at the same time. Here, the outer housing or the outer contour of a directly molded concentric collar both the axial and the radial mounting of the inner contour of the torsion ensure and thus allow the only remaining degree of freedom, the rotation of the inner to the outer contour. In particular, the following advantageous embodiments can be provided:
• - Storage of the sun gear of the second translation stage on a bolt which is attached directly to the inner contour of the torsion element or formed there directly;
• - Storage of the sun gear of the third stage on a bolt, which is attached directly to the inner contour of the torsion element or formed there directly.
• - Storage of the planet carrier of the first gear stage on the drive side either inwardly on a common with a rotor shaft of the electric motor rotating or formed from this bolt or radially on the outside of a housing of the electric motor;
• - Storage of the planet carrier of the second gear stage on the drive side via a bearing, which is supported on the bearing of the associated sun gear of the second gear ratio, in turn rotatably mounted on the previously described, the inner contour of the torsion associated bolt is mounted;
• - Accordingly, the described three-stage planetary gear can be formed two or more than three stages.

Brief description of the figures

The invention is based on the in the 1 and 2 illustrated embodiments explained in more detail. Showing:

1 a longitudinal section through a planetary gear with a mounted on a rotor shaft of an electric motor translation stage and

2 a longitudinal section through a planetary gear with a mounted on a housing of an electric motor translation stage.

Detailed description of the figures

The 1 shows the planet gear arranged about the rotation axis x 1 with the entrance part 2 and the output part 3 and the intermediately arranged therebetween transmission stages I, II, III in longitudinal section. The rotor shaft 4 with the end to the bolt 5 trained sun wheel 6 represents in the embodiment shown, the input part 2 dar. The rotor shaft 4 is part of an electric motor, not shown, with the planetary gear 1 , the torsion element 7 and the housing 11 forms an electromechanical actuator, for example for a roll stabilizer. The torsion element 7 forms the starting part 3 and contains the inner contour 8th and the outer contour 9 as well as not visible in detail, in the circumferential direction effectively arranged between these energy storage 7a , Further details on the function and structure of corresponding torsion elements, for example, the DE 10 2009 006 385 A1 be removed.

The outer contour 9 is by means of storage 10 , For example, a sliding or rolling bearing, preferably a fixed bearing for axially fixed and rotatable receiving the outer contour 9 on the housing 11 stored. In the case 11 are one-piece the gears 12 . 13 . 14 for the ring gears 15 . 16 . 17 the translation stages I, II, III incorporated. The inner contour 8th is by means of storage 18 like plain bearing between the inner contour 8th radially surrounding outer annular collar 18a one-sided axially fixed and rotatably received on the outer contour. The inner contour 8th Contains one-piece or rigidly connected as pressed on a bolt 19 that by means of the bearings 20 . 21 like sliding bearings graded the sun gears 22 . 23 the translation stages II, III rotatably accommodates.

The planet carrier 24 the first translation stage I is in the illustrated embodiment by means of storage 25 Preferably, a roller-bearing fixed bearing such as deep groove ball bearings, angular contact ball bearings or the like on the rotor shaft 4 stored. Warehousing 25 can also be a plain bearing. On the opposite side of the planet carrier 24 with the between ring gear 15 and sun gear 6 meshing planet wheels 26 is between the planet carrier 24 the first translation stage I and the planet carrier 27 the translation stage II with the between the ring gear 16 and the sun wheel 22 meshing planet wheels 29 warehousing 28 intended. Warehousing 28 is radially outside and substantially within the axial space of the storage 20 arranged. Warehousing 28 is preferably designed as a fixed bearing in the form of a roller bearing such as deep groove ball bearings, angular contact ball bearings and the like, or as plain bearings.

The torque flow takes place starting from the input part 2 to the first gear stage I and the second and third gear stages II, III to the output part 3 , This is the sun gear 6 from the rotor shaft 4 driven. This drives the planet wheels 26 and thus the planet carrier 24 at. This drives the sun wheel 22 the second translation stage. About the planet wheels 29 and the planet carrier 27 becomes the sun wheel 23 the third gear stage III driven. This finally drives over the planet wheels 30 the planet carrier 31 in the inner contour 8th integrated, the torsion element 7 and thus the starting part 3 at. By the nesting of the bearings 18 . 20 . 21 . 25 . 28 with partial radial and axial override, the epicyclic gear can 1 in conjunction with the one-piece to the housing 11 recorded ring gears 15 . 16 . 17 particularly compact, that is to be formed with a small axial space requirement.

The 2 shows that the planetary gear 1 of the 1 similar epicyclic gearboxes 1a in section along the axis of rotation x. The only difference is the storage 25a of the planet carrier 24a on the housing section 32a the electric motor, not shown, so that the rotor shaft 4a can be stored more easily.

LIST OF REFERENCE NUMBERS

1

 Planetary gear

1a

 Planetary gear

2

 introductory

3

 output portion

4

 rotor shaft

4a

 rotor shaft

5

 bolt

6

 sun

7

 torsion

7a

 energy storage

8th

 inner contour

9

 outer contour

10

 storage

11

 casing

12

 gearing

13

 gearing

14

 gearing

15

 ring gear

16

 ring gear

17

 ring gear

18

 storage

18a

 collar

19

 bolt

20

 storage

21

 storage

22

 sun

23

 sun

24

 planet carrier

24a

 planet carrier

25

 storage

25a

 storage

26

 planet

27

 planet carrier

28

 storage

29

 planet

30

 planet

31

 planet carrier

32a

 housing section

I

 translation stage

II

 translation stage

III

 translation stage

x

 axis of rotation

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102009006385 A1 [0003, 0012, 0016]

Claims (10)

Planetary gear ( 1 . 1a ) in particular for an electromechanical actuator having an input part ( 2 ) and an output part ( 3 ) and with at least two arranged between these translation stages (I, II, III) comprising components consisting of at least one ring gear ( 15 . 16 . 17 ), one of a translation stage (I, II, III) associated sun gear ( 6 . 22 . 23 ) and one in each case a translation stage (I, II, III) associated with planet carrier ( 24 . 27 . 31 ) distributed over the circumference, between sun gear ( 6 . 22 . 23 ) and ring gear ( 15 . 16 . 17 ) meshing planet wheels ( 26 . 29 . 30 ), characterized in that at least two components by means of radially and / or axially overlapping bearings ( 10 . 18 . 20 . 21 . 28 . 25 . 25a on each other and independent of a bearing relative to the at least one ring gear ( 15 . 16 . 17 ) are stored. Planetary gear ( 1 . 1a ) according to claim 1, characterized in that the ring gears ( 15 . 16 . 17 ) All gear ratios (I, II, III) are provided as a one-piece ring gear. Planetary gear ( 1 . 1a ) according to claim 1 or 2, characterized in that the at least two components on the input side and / or output side on a radially inwardly arranged bolt ( 5 . 19 ) are stored directly or indirectly. Planetary gear ( 1 . 1a ) according to claim 3, characterized in that all sun gears ( 6 . 22 . 23 ) on the bolt ( 5 . 19 ) and at least two sun gears ( 6 . 22 . 23 ) on different bolts ( 5 . 19 ) are stored. Planetary gear ( 1 . 1a ) according to one of claims 1 to 4, characterized in that between input part ( 2 ) or output part ( 3 ) and subsequent translation stage (III) a torsion element ( 7 ) is arranged with two mutually limited against the action of a circumferentially effective energy storage rotatable components, one of these components a planet carrier ( 31 ) receives this translation stage (III) and an axial and radial bearing ( 10 ) is provided between the components. Planetary gear ( 1 ) according to one of claims 1 to 5, characterized in that an input part ( 3 ) of the epicyclic gearbox ( 1 ) with a rotor shaft ( 4 ) of an electric motor is rotationally connected and the planet carrier ( 24 ) by means of the sun gear ( 6 ) with the rotor shaft ( 4 ) associated translation stage (I) on the rotor shaft ( 4 ) is rotatably mounted. Planetary gear ( 1a ) according to one of claims 1 to 5, characterized in that an input part of the planetary gear ( 1a ) is rotationally connected to a rotor shaft of an electric motor and the planet carrier ( 24a ) connected by means of the sun gear with the rotor shaft translation stage on a housing portion ( 32a ) of the electric motor is rotatably mounted. Planetary gear ( 1 . 1a ) according to one of claims 1 to 7, characterized in that two planet carriers ( 24 . 24a . 27 ) axially adjacent translation stages (I, II) are rotatably mounted on each other. Planetary gear ( 1 . 1a ) according to claim 8, characterized in that a storage ( 28 ) of the two planet carriers ( 24 . 24a . 27 ) radially outside of a bearing ( 20 ) of the sun gear ( 22 ) one of the translation stages (II) on a bolt ( 19 ) is arranged. Planetary gear ( 1 . 1a ) according to one of claims 3 to 9, characterized in that between the sun gears ( 22 . 23 ) and at least one of the bolts ( 19 ) Bearings and between the other components of the gear ratios (I, II) rolling bearings, in particular fixed bearings are provided.

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