EP4623224A1 - Input gear stage for an epicyclic gear box - Google Patents

Input gear stage for an epicyclic gear box

Info

Publication number
EP4623224A1
EP4623224A1 EP22822445.7A EP22822445A EP4623224A1 EP 4623224 A1 EP4623224 A1 EP 4623224A1 EP 22822445 A EP22822445 A EP 22822445A EP 4623224 A1 EP4623224 A1 EP 4623224A1
Authority
EP
European Patent Office
Prior art keywords
input
gear
pinion
gear wheel
stage
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP22822445.7A
Other languages
German (de)
French (fr)
Inventor
Ingo Schulz
Lijun CAO
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SKF AB
Original Assignee
SKF AB
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by SKF AB filed Critical SKF AB
Publication of EP4623224A1 publication Critical patent/EP4623224A1/en
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
    • F16H1/22—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/06—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with parallel axes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/06—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with parallel axes
    • F16H1/08—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with parallel axes the members having helical, herringbone, or like teeth

Definitions

  • the present invention relates to an input gear stage for an epicyclic gear box according to claim 1 and to an epicyclic gear box having such an input gear stage according to claim 8.
  • High precision gear boxes which may be used for example in industrial robotics or in machine tools, usually consist of a two-stage design.
  • the first stage also called input gear stage, is the stage that is transforming the input speed and torque from the motor.
  • Such an input gear stage can be designed like a spur gear with a sun-like input pinion, which drives one or several planet-like gears.
  • the input pinion may be eccentrically positioned and may drive a larger gear, that then acts on a sun-like pinion or e.g., on the carrier of the high precision gear box.
  • the gear wheel is usually an integral part of the gear box and is limited in its diameter. That may be the case for example due to geometrical restrictions, which result inter alia from the requirement of mounting interfaces.
  • the diameter of the pinion and the gear wheel in turn is defined by the teeth number and the modulus of the gear.
  • a large modulus limits the teeth number and therefore the reduction ratio of the input gear stage.
  • a high teeth number is used for enabling a high reduction ratio with a given diameter limit.
  • a high teeth number limits the size of the modulus and therefore the torque capacity of the input gear stage. It is therefore an object of the present invention to provide an eccentrically driven input gear stage which is capable of supporting a high reduction ratio and/or a high torque also for a limited diameter size of an input pinion and the gear wheel.
  • the eccentrically driven input gear stage may be used in any kind of epicyclic gear box which comprises an eccentrically arranged input drive.
  • an epicyclic gear box may be used for high precision gear boxes, in particular in the field of industrial robotics.
  • the input gear stage For transferring a driving force from the input drive to the input gear stage, the input gear stage comprises an input pinion and a gear wheel.
  • the input pinion is eccentrically positioned in relation to the gear wheel and is configured to transfer a driving force from the input drive, for example an electrical motor, to the gear wheel.
  • the gear wheel may be attached to a sun gear or a carrier which may be part of a second stage of the epicyclic gear box.
  • the input drive force may be transferred from the input pinion via the gear wheel to the second stage of the epicyclic gear box.
  • the herein described input gear stage comprises two intermediate pinions.
  • the two intermediate pinions are arranged between the input pinion and the gear wheel for transferring the movement of the input pinion to the gear wheel.
  • the input drive is transferred from the input pinion to the intermediate pinions and then to the gear wheel.
  • the herein described input gear stage has two load paths: one from the input pinion via the first intermediate pinion to the gear wheel and one from the input pinion via the second intermediate pinion to the gear wheel.
  • the stress onto the contact between input pinion and gear wheel is reduced as the input pinion has contact with (or more precisely meshes with) the two intermediate pinions and the gear wheel also has contact with or meshes with the two intermediate pinions.
  • the load path, and the corresponding stress or loading is thus divided in two so that the stress or loading onto the input pinion as well as the gear wheel is reduced.
  • Having two intermediate pinions not only adds a second load path but also has the advantage that at least two teeth pairs are in contact. More precisely, the input pinion is in contact with the first intermediate pinion and is simultaneously in contact with the second intermediate pinion.
  • the gear wheel is in contact with the first intermediate pinion and is simultaneously in contact with the second intermediate pinion.
  • Having two load paths and an increased contact between the pinions and gear wheel allows for either a higher torque load or a larger reduction ratio or both while at the same time, the loading onto the input pinion and/or the gear wheel is reduced or at least not increased.
  • the intermediate pinions have the same dimensional size and/or same number of teeth. This provides the advantage that the same intermediate pinion may be used, which reduces the manufacturing cost.
  • the input pinion may also have same dimensional size and/or same number of teeth, further reducing the manufacturing cost.
  • Fig. 2 a schematical top view of a second embodiment of an eccentrically driven input gear stage
  • Fig. 3 a schematical top view of a third embodiment of an eccentrically driven input gear stage.
  • the input gear stage 1 further comprises two intermediate pinions 6, 8. As can be seen in Figs. 1 to 3, the intermediate pinions 6, 8 are arranged between the input pinion 4 and the gear wheel 2 for transferring the movement of the input pinion 4 to the gear wheel 2.
  • the two intermediate pinions 6, 8 may be preloaded with the input pinion 2 in opposite directions.
  • gearings 10, 12, 14, 16 are shown as straight gearings, they may also be helical gearings when suitable.
  • the gear wheel 2, the input pinion 4 and/or the intermediate pinions 6, 8 each may have an inner hole 18, 20, 22, 24. These inner holes 18, 20, 22, 24 may be used for supporting the gear wheel 2, the input pinion 4 and/or the intermediate pinions 6, 8 or may be used as passage for cables or the like. The inner holes 18, 20, 22, 24 may also be omitted when suitable.
  • the input pinion 4 and the intermediate pinions 6, 8 may have the same dimensional size.
  • the input pinion 4 and the intermediate pinions 6, 8 may be identical. This has the advantage that only one kind of pinion needs to be manufactured. This may reduce the manufacturing cost and may also save costs in case of a replacement of the pinions.
  • resonance frequencies may increase.
  • Figs. 1, 2 and 3 may also be combined.
  • differently sized pinions 4, 6, 8 may be used.
  • the herein described input gear stage uses two intermediate pinions, interposed between the input pinion and the gear wheel, which provides two load paths instead of only one single load path.
  • the two load paths allow a smaller modulus of the input pinion and/or the intermediate pinions, which in turn allows for more teeth and therefore a higher reduction ratio.
  • the torque capacity of the input gear stage may be increased.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)

Abstract

Disclosed is an eccentrically driven input gear stage (1) for an epicyclic gear box, the input gear stage (1) comprising a gear wheel (2) and an input pinion (4), wherein the input pinion (4) is eccentrically positioned in relation to the gear wheel (2) and is configured to transfer a driving force to the gear wheel (2), wherein the input gear stage (1) comprises two intermediate pinions (6, 8) being arranged between the input pinion (4) and the gear wheel (2) for transferring the movement of the input pinion (4) to the gear wheel (2).

Description

D e s c r i p t i o n
Input gear stage for an epicyclic gear box
The present invention relates to an input gear stage for an epicyclic gear box according to claim 1 and to an epicyclic gear box having such an input gear stage according to claim 8.
High precision gear boxes, which may be used for example in industrial robotics or in machine tools, usually consist of a two-stage design. The first stage, also called input gear stage, is the stage that is transforming the input speed and torque from the motor. Such an input gear stage can be designed like a spur gear with a sun-like input pinion, which drives one or several planet-like gears. Alternatively, the input pinion may be eccentrically positioned and may drive a larger gear, that then acts on a sun-like pinion or e.g., on the carrier of the high precision gear box.
In case of the eccentrically positioned pinion, the gear wheel is usually an integral part of the gear box and is limited in its diameter. That may be the case for example due to geometrical restrictions, which result inter alia from the requirement of mounting interfaces. The diameter of the pinion and the gear wheel in turn is defined by the teeth number and the modulus of the gear. Thus, for enabling a high torque with a given diameter limit, a large modulus is used. However, a large modulus limits the teeth number and therefore the reduction ratio of the input gear stage. In turn, for enabling a high reduction ratio with a given diameter limit, a high teeth number is used. However, such a high teeth number limits the size of the modulus and therefore the torque capacity of the input gear stage. It is therefore an object of the present invention to provide an eccentrically driven input gear stage which is capable of supporting a high reduction ratio and/or a high torque also for a limited diameter size of an input pinion and the gear wheel.
This object is solved by an eccentrically driven input gear stage for an epicyclic gear box according to claim 1 and an epicyclic gear box according to claim 8.
The eccentrically driven input gear stage may be used in any kind of epicyclic gear box which comprises an eccentrically arranged input drive. For example, such an epicyclic gear box may be used for high precision gear boxes, in particular in the field of industrial robotics. For transferring a driving force from the input drive to the input gear stage, the input gear stage comprises an input pinion and a gear wheel. The input pinion is eccentrically positioned in relation to the gear wheel and is configured to transfer a driving force from the input drive, for example an electrical motor, to the gear wheel. The gear wheel may be attached to a sun gear or a carrier which may be part of a second stage of the epicyclic gear box. Thus, the input drive force may be transferred from the input pinion via the gear wheel to the second stage of the epicyclic gear box.
In order to provide an input gear stage which can support a high reduction ratio and/or a high torque, the herein described input gear stage comprises two intermediate pinions. The two intermediate pinions are arranged between the input pinion and the gear wheel for transferring the movement of the input pinion to the gear wheel. Thus, the input drive is transferred from the input pinion to the intermediate pinions and then to the gear wheel. Instead of having one load path from the input pinion to the gear wheel, the herein described input gear stage has two load paths: one from the input pinion via the first intermediate pinion to the gear wheel and one from the input pinion via the second intermediate pinion to the gear wheel. By having two load paths, the stress onto the contact between input pinion and gear wheel is reduced as the input pinion has contact with (or more precisely meshes with) the two intermediate pinions and the gear wheel also has contact with or meshes with the two intermediate pinions. The load path, and the corresponding stress or loading, is thus divided in two so that the stress or loading onto the input pinion as well as the gear wheel is reduced. Having two intermediate pinions not only adds a second load path but also has the advantage that at least two teeth pairs are in contact. More precisely, the input pinion is in contact with the first intermediate pinion and is simultaneously in contact with the second intermediate pinion. The same applies in an analogue manner to the gear wheel, i.e., the gear wheel is in contact with the first intermediate pinion and is simultaneously in contact with the second intermediate pinion. Having two load paths and an increased contact between the pinions and gear wheel allows for either a higher torque load or a larger reduction ratio or both while at the same time, the loading onto the input pinion and/or the gear wheel is reduced or at least not increased.
According to an embodiment, the intermediate pinions have the same dimensional size and/or same number of teeth. This provides the advantage that the same intermediate pinion may be used, which reduces the manufacturing cost. Advantageously, the input pinion may also have same dimensional size and/or same number of teeth, further reducing the manufacturing cost.
Alternatively, the intermediate pinions have different dimensional sizes and/or a different number of teeth. When two differently sized intermediate pinions are used, the risk of resonance frequencies (which may occur in the case of equally sized intermediate pinions) may be reduced or eliminated.
Basically, the size of the input pinion as well as the intermediate pinions is a matter of design and load considerations. When limited installation space is available, the sizes of the input pinion and/or intermediate pinions may be reduced. When more installation space is available, the sizes of the input pinion and/or intermediate pinions may be increased, allowing an improved load distribution.
The input pinion, the intermediate pinions, and the gear wheel each may have an outer gearing, wherein the gearing of each intermediate pinion meshes with the gearing of the input pinion and the gearing of the gear wheel. Also in this case, the precise arrangement may be based on design considerations, taking into account the available installation space. For example, when the installation space is limited, the input pinion may be arranged between the two intermediate pinions, as near as possible to the gear wheel without meshing with the gear wheel. When more installation space is available, the input pinion may be arranged as far away from the gear wheel as possible, as long as the input pinion can mesh with both intermediate pinions.
The gearings of the input pinion, the intermediate pinions as well as the gear wheel may be straight or may be helical. All gearings have to be the same, i.e., either helical or straight. The kind of gearing may be chosen as suitable.
In case of that no axial reaction of the pinions is allowed, or the diameter is limited, a straight kind of gearing could be preferred. Especially when a high torque, low noise or low vibrations are required, a helical kind of gearing may become advantageous.
As described above, the input gear stage may be part of an epicyclic gear box. Thus, the gear wheel may be coupled to a further wheel of the epicyclic gear box, for example may be coupled to a sun gear or a carrier of the epicyclic gear box. The input pinion may be coupled to an input drive, in particular to an electrical motor. The input drive may be arranged eccentrically and may particularly be configured for driving the input pinion in an eccentrical manner in relation to the gear wheel.
According to a further aspect, an epicyclic gear box is disclosed which comprises an input gear stage as described above. In addition, the epicyclic gear box comprises at least a further stage, for example an output stage. As described above, the gear wheel of the input gear stage is coupled to a further wheel of the output stage and the input pinion of the input gear stage is coupled to an input drive.
By having such an input gear stage, the contact force between the input pinion and the intermediate pinions is less than a contact force being present between the input pinion and the gear wheel when no intermediate pinions are used, and the input pinion directly contacts the gear wheel. For example, the contact force may be reduced by about 50%. Also, the contact pressure may be reduced, for example reduced to about 60% to 70%, in comparison with previously used designs without intermediate pinions.
By reducing the loading, contact force and/or contact pressure, the service life of the input gear stage, and thus of the overall epicyclic gear box may be increased. Further, as the installation space requirements of the input gear stage may be reduced, as described above, also the installation space requirements of the overall epicyclic gear box may be reduced. This allows the utilization of the gear box also in environments having only small installation space. As the gear box may support higher torques and/or higher reduction ratios and may be built in a smaller manner than previously used gear boxes at the same time, such a gear box may particular be used in industrial robotics or automotive applications which typically have high constraints regarding installation space and high requirements regarding torque and/or reduction ratio.
Further preferred embodiments are defined in the dependent claims as well as in the description and the figures. Thereby, elements described or shown in combination with other elements may be present alone or in combination with other elements without departing from the scope of protection.
In the following, preferred embodiments of the invention are described in relation to the drawings, wherein the drawings are exemplarily only, and are not intended to limit the scope of protection. The scope of protection is defined by the accompanied claims, only.
The figures show:
Fig. 1 : a schematical top view of a first embodiment of an eccentrically driven input gear stage;
Fig. 2: a schematical top view of a second embodiment of an eccentrically driven input gear stage; and
Fig. 3 : a schematical top view of a third embodiment of an eccentrically driven input gear stage.
In the following same or similar functioning elements are indicated with the same reference numerals.
Fig. 1 shows an eccentrically driven input gear stage 1. Such an input gear stage 1 may be used for example in an epicyclic gear box, which can be used inter alia in (industrial) robotics or any other kind of application in different technical fields, like automotive. The epicyclic gear box may be for example a high precision gear box. Independent of the kind of application, the gear box is eccentrically driven, which means that the input gear stage 1 is driven by a motor being eccentrically arranged with respect to a main rotational axis of a gear wheel 2 being connected to a further stage of the gear box.
The gear wheel 2 may for example be connected to a carrier or a sun gear of a further gear box stage. The gear wheel 2 is driven by an input pinion 4. The input pinion 4 is eccentrically positioned in relation to the gear wheel 2 and is configured to transfer a driving force, for example from an electrical motor or the like, to the gear wheel 2.
In order to support higher torques and/or reduction ratios than in previously used input gear stages, the input gear stage 1 further comprises two intermediate pinions 6, 8. As can be seen in Figs. 1 to 3, the intermediate pinions 6, 8 are arranged between the input pinion 4 and the gear wheel 2 for transferring the movement of the input pinion 4 to the gear wheel 2.
For transferring the movement, the gear wheel 2 has an outer gearing 10, the input pinion 4 has an outer gearing 12 and the intermediate pinions 6, 8 also have outer gearings 14, 16. The gearing 12 of the input pinion 4 meshes with the gearings 14, 16 of the intermediate pinions 6, 8 and the gearings 14, 16 of the intermediate pinions 6, 8 mesh with the gearing 10 of the gear wheel 2. Thus, when the input pinion 4 is driven by an input drive, the movement of the input pinion 4 is transferred to the gear wheel 2 via the interposed intermediate pinions 6, 8.
By having the two intermediate pinions 6, 8, not only one single load path is formed between the input pinion 4 and the gear wheel 2, but instead two load paths are formed: the first load path is formed from the input pinion 4 via the first intermediate pinion 6 to the gear wheel 2 and the second load path is formed from the input pinion 4 via the second intermediate pinion 8 to the gear wheel 2. More precisely, the first and the second load paths are formed due to the meshing of the gearings 12, 14, 10 and 12, 16, 10 and the corresponding contact between the input pinion 4, the intermediate pinion 6 and the gear wheel 2 as well as the contact between the input pinion 4, the intermediate pinion 8 and the gear wheel 2.
Having two load paths splits the overall load onto the two load paths, effectively decreasing the loading, contact force and/or contact pressure acting on the input pinion 4 and the gear when 2. Thus, a smaller pinion 4 may be used in contrast to previous input gear stages while supporting the same amount of loading, contact force and/or contact pressure. A smaller input pinion 4 results also in a smaller overall diameter of the input gear stage 1, reducing the installation space requirements. Further, the arrangement of input pinion 4, intermediate pinions 6, 8 and gear wheel 2 supports a higher reduction ratio and higher torque as the loading on each single element of the input gear stage 1 is reduced due to the two load paths.
In addition, as two intermediate pinions 6, 8 are used, backlash may be eliminated in the input gear stage 1. For this purpose, the two intermediate pinions 6, 8 may be preloaded with the input pinion 2 in opposite directions.
It should be noted that, although the gearings 10, 12, 14, 16 are shown as straight gearings, they may also be helical gearings when suitable. Further, the gear wheel 2, the input pinion 4 and/or the intermediate pinions 6, 8 each may have an inner hole 18, 20, 22, 24. These inner holes 18, 20, 22, 24 may be used for supporting the gear wheel 2, the input pinion 4 and/or the intermediate pinions 6, 8 or may be used as passage for cables or the like. The inner holes 18, 20, 22, 24 may also be omitted when suitable.
As shown in Fig. 1, the input pinion 4 and the intermediate pinions 6, 8 may have the same dimensional size. Advantageously, the input pinion 4 and the intermediate pinions 6, 8 may be identical. This has the advantage that only one kind of pinion needs to be manufactured. This may reduce the manufacturing cost and may also save costs in case of a replacement of the pinions. However, when identical pinions 4, 6, 8 are used, resonance frequencies may increase.
Thus, in a further embodiment, the input pinion 4 and the intermediate pinions 6, 8 may have different sizes. In this case, at least one pinion 4, 6, 8 is different than the others, but also all three pinions 4, 6, 8 may be different. For example, as shown in Fig. 2, the intermediate pinion 6 may be smaller than the input pinion 4 and the intermediate pinion 8. Such an arrangement may reduce resonance frequencies but still provides the advantage of having two load paths. In a further embodiment, the input pinion 4 may be arranged more closely to the gear wheel 2. As shown in Fig. 3, the input pinion 4 is arranged as closely to the gear wheel 2 as possible, without contacting the gear wheel 2. Still, two load paths are provided via the two intermediate pinions 6, 8, but at the same time, the overall diameter of the input gear stage 1 is further reduced. Such an arrangement may be advantageously when the installation space of the input gear stage 1 is strictly limited.
It should be noted that the embodiments of Figs. 1, 2 and 3 may also be combined. For example, in the embodiment of Fig. 3, differently sized pinions 4, 6, 8 may be used.
In summary, the herein described input gear stage uses two intermediate pinions, interposed between the input pinion and the gear wheel, which provides two load paths instead of only one single load path. The two load paths allow a smaller modulus of the input pinion and/or the intermediate pinions, which in turn allows for more teeth and therefore a higher reduction ratio. As the input gear stage allows more load (due to the load split onto two load paths, thus less load on each path), the torque capacity of the input gear stage may be increased.
Reference numerals
1 Input gear stage
2 gear wheel
4 input pinion
6 intermediate pinion
8 intermediate pinion
10 gearing
12 gearing
14 gearing
16 gearing
18 inner hole
20 inner hole
22 inner hole
24 inner hole

Claims

C l a i m s
Input gear stage for an epicyclic gear box Eccentrically driven input gear stage (1) for an epicyclic gear box, the input gear stage (1) comprising a gear wheel (2) and an input pinion (4), wherein the input pinion (4) is eccentrically positioned in relation to the gear wheel (2) and is configured to transfer a driving force to the gear wheel (2), characterized in that the input gear stage (1) comprises two intermediate pinions (6, 8) being arranged between the input pinion (4) and the gear wheel (2) for transferring the movement of the input pinion (4) to the gear wheel (2). Input gear stage according to claim 1, wherein the intermediate pinions (6, 8) have the same dimensional size and/or same number of teeth. Input gear stage according to claim 1, wherein the intermediate pinions (6, 8) have different dimensional sizes and/or a different number of teeth. Input gear stage according to any one of the preceding claims, wherein the input pinion (4), the intermediate pinions (6, 8) and the gear wheel (2) each have an outer gearing (10, 12, 14, 16), wherein the gearing (14, 16) of each intermediate pinion (6, 8) meshes with the gearing (12) of the input pinion (4) and the gearing (10) of the gear wheel (2). Input gear stage according to claim 4, wherein the gearings (10, 12, 14, 16) of the input pinion (4), the intermediate pinions (6, 8) and the gear wheel (2) are straight. Input gear stage according to claim 4, wherein the gearings (10, 12, 14, 16) of the input pinion (4), the intermediate pinions (6, 8) and the gear wheel (2) are helical. Input gear stage according to any one of the preceding claims, wherein the gear wheel (2) is couplable to a further wheel of the epicyclic gear box and wherein the input pinion (4) is couplable to an input drive, in particular to an electrical motor. Epicyclic gear box comprising an input gear stage (1) according to any one of the preceding claims and an output stage, wherein the gear wheel (2) of the input gear stage (1) is coupled to a further wheel of the output stage and wherein the input pinion (4) of the input gear stage (1) is coupled to an input drive.
EP22822445.7A 2022-11-25 2022-11-25 Input gear stage for an epicyclic gear box Pending EP4623224A1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2022/083325 WO2024110054A1 (en) 2022-11-25 2022-11-25 Input gear stage for an epicyclic gear box

Publications (1)

Publication Number Publication Date
EP4623224A1 true EP4623224A1 (en) 2025-10-01

Family

ID=84488184

Family Applications (1)

Application Number Title Priority Date Filing Date
EP22822445.7A Pending EP4623224A1 (en) 2022-11-25 2022-11-25 Input gear stage for an epicyclic gear box

Country Status (3)

Country Link
EP (1) EP4623224A1 (en)
CN (1) CN120035722A (en)
WO (1) WO2024110054A1 (en)

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3610065A (en) * 1969-10-23 1971-10-05 Teru Hayashi Power transmission gear system
JPS4953173U (en) * 1972-08-25 1974-05-10
DE4434237A1 (en) * 1994-09-24 1996-03-28 Deere & Co Vehicle axle with wheels powered by individual electric drives
DE19604730A1 (en) * 1996-02-09 1997-08-14 Zahnradfabrik Friedrichshafen Portal axis
DE19852394A1 (en) * 1998-11-13 2000-05-18 Zahnradfabrik Friedrichshafen Portal drive for portal axes, especially for drive axes, for a bus drive
DE10006021A1 (en) * 2000-02-11 2001-08-16 Zahnradfabrik Friedrichshafen End gear for a portal axis
US20070295136A1 (en) * 2006-05-05 2007-12-27 The Regents Of The University Of California Anti-backlash gear system
CN102996715A (en) * 2011-09-19 2013-03-27 无锡市阳通机械设备有限公司 Power transmission mechanism
CN110682790B (en) * 2018-07-04 2021-12-07 比亚迪股份有限公司 Vehicle transmission device and vehicle

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Publication number Publication date
CN120035722A (en) 2025-05-23
WO2024110054A1 (en) 2024-05-30

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