WO2024110054A1 - Étage d'engrenage d'entrée pour une boîte de vitesses épicycloïdale - Google Patents

Étage d'engrenage d'entrée pour une boîte de vitesses épicycloïdale Download PDF

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Publication number
WO2024110054A1
WO2024110054A1 PCT/EP2022/083325 EP2022083325W WO2024110054A1 WO 2024110054 A1 WO2024110054 A1 WO 2024110054A1 EP 2022083325 W EP2022083325 W EP 2022083325W WO 2024110054 A1 WO2024110054 A1 WO 2024110054A1
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WO
WIPO (PCT)
Prior art keywords
input
gear
pinion
gear wheel
stage
Prior art date
Application number
PCT/EP2022/083325
Other languages
English (en)
Inventor
Ingo Schulz
Lijun CAO
Original Assignee
Aktiebolaget Skf
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 Aktiebolaget Skf filed Critical Aktiebolaget Skf
Priority to PCT/EP2022/083325 priority Critical patent/WO2024110054A1/fr
Publication of WO2024110054A1 publication Critical patent/WO2024110054A1/fr

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.
  • the intermediate pinions have different dimensional sizes and/or a different number of teeth.
  • the risk of resonance frequencies may be reduced or eliminated.
  • 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.
  • 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.
  • the input gear stage may be part of an epicyclic gear box.
  • 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.
  • an epicyclic gear box which comprises an input gear stage as described above.
  • the epicyclic gear box comprises at least a further stage, for example an output stage.
  • 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.
  • 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.
  • the contact force may be reduced by about 50%.
  • the contact pressure may be reduced, for example reduced to about 60% to 70%, in comparison with previously used designs without intermediate pinions.
  • 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.
  • 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
  • Fig. 3 a schematical top view of a third embodiment of an eccentrically driven input gear stage.
  • 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.
  • 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.
  • 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 gear wheel 2 has an outer gearing 10
  • the input pinion 4 has an outer gearing 12
  • 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.
  • the first load path is formed from the input pinion 4 via the first intermediate pinion 6 to the gear wheel 2
  • 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.
  • 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.
  • 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.
  • 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.
  • the input pinion 4 and the intermediate pinions 6, 8 may have different sizes.
  • at least one pinion 4, 6, 8 is different than the others, but also all three pinions 4, 6, 8 may be different.
  • the intermediate pinion 6 may be smaller than the input pinion 4 and the intermediate pinion 8.
  • the input pinion 4 may be arranged more closely to the gear wheel 2.
  • the input pinion 4 is arranged as closely to the gear wheel 2 as possible, without contacting the gear wheel 2.
  • 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.
  • 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

La présente invention concerne un étage d'engrenage d'entrée à entraînement excentrique (1) pour une boîte de vitesses épicycloïdale, l'étage d'engrenage d'entrée (1) comprenant une roue d'engrenage (2) et un pignon d'entrée (4), le pignon d'entrée (4) étant positionné de manière excentrique par rapport à la roue d'engrenage (2) et étant configuré pour transférer une force d'entraînement à la roue d'engrenage (2), l'étage d'engrenage d'entrée (1) comprenant deux pignons intermédiaires (6, 8) agencés entre le pignon d'entrée (4) et la roue d'engrenage (2) pour transférer le mouvement du pignon d'entrée (4) à la roue d'engrenage (2).
PCT/EP2022/083325 2022-11-25 2022-11-25 Étage d'engrenage d'entrée pour une boîte de vitesses épicycloïdale WO2024110054A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/EP2022/083325 WO2024110054A1 (fr) 2022-11-25 2022-11-25 Étage d'engrenage d'entrée pour une boîte de vitesses épicycloïdale

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2022/083325 WO2024110054A1 (fr) 2022-11-25 2022-11-25 Étage d'engrenage d'entrée pour une boîte de vitesses épicycloïdale

Publications (1)

Publication Number Publication Date
WO2024110054A1 true WO2024110054A1 (fr) 2024-05-30

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PCT/EP2022/083325 WO2024110054A1 (fr) 2022-11-25 2022-11-25 Étage d'engrenage d'entrée pour une boîte de vitesses épicycloïdale

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Citations (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 (fr) * 1972-08-25 1974-05-10
DE4434237A1 (de) * 1994-09-24 1996-03-28 Deere & Co Fahrzeugachse mit elektrischem Einzelradantrieb
DE19604730A1 (de) * 1996-02-09 1997-08-14 Zahnradfabrik Friedrichshafen Portalachse
DE19852394A1 (de) * 1998-11-13 2000-05-18 Zahnradfabrik Friedrichshafen Portaltrieb für Portalachsen, insbesondere für Antriebsachsen, für einen Bus-Antrieb
WO2001059332A1 (fr) * 2000-02-11 2001-08-16 Zf Friedrichshafen Ag Transmission terminale pour pont deporte
US20070295136A1 (en) * 2006-05-05 2007-12-27 The Regents Of The University Of California Anti-backlash gear system
CN102996715A (zh) * 2011-09-19 2013-03-27 无锡市阳通机械设备有限公司 一种动力传动机构
EP3815950A1 (fr) * 2018-07-04 2021-05-05 BYD Company Limited Appareil de transmission de véhicule, et véhicule

Patent Citations (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 (fr) * 1972-08-25 1974-05-10
DE4434237A1 (de) * 1994-09-24 1996-03-28 Deere & Co Fahrzeugachse mit elektrischem Einzelradantrieb
DE19604730A1 (de) * 1996-02-09 1997-08-14 Zahnradfabrik Friedrichshafen Portalachse
DE19852394A1 (de) * 1998-11-13 2000-05-18 Zahnradfabrik Friedrichshafen Portaltrieb für Portalachsen, insbesondere für Antriebsachsen, für einen Bus-Antrieb
WO2001059332A1 (fr) * 2000-02-11 2001-08-16 Zf Friedrichshafen Ag Transmission terminale pour pont deporte
US20070295136A1 (en) * 2006-05-05 2007-12-27 The Regents Of The University Of California Anti-backlash gear system
CN102996715A (zh) * 2011-09-19 2013-03-27 无锡市阳通机械设备有限公司 一种动力传动机构
EP3815950A1 (fr) * 2018-07-04 2021-05-05 BYD Company Limited Appareil de transmission de véhicule, et véhicule

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