WO2014097855A1 - Mécanisme d'engrenage planétaire - Google Patents

Mécanisme d'engrenage planétaire Download PDF

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Publication number
WO2014097855A1
WO2014097855A1 PCT/JP2013/082116 JP2013082116W WO2014097855A1 WO 2014097855 A1 WO2014097855 A1 WO 2014097855A1 JP 2013082116 W JP2013082116 W JP 2013082116W WO 2014097855 A1 WO2014097855 A1 WO 2014097855A1
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WO
WIPO (PCT)
Prior art keywords
planetary gear
tooth surface
internal gear
teeth
gear
Prior art date
Application number
PCT/JP2013/082116
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English (en)
Japanese (ja)
Inventor
秀行 山口
西村　光宣
Original Assignee
日立オートモティブシステムズ株式会社
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Filing date
Publication date
Application filed by 日立オートモティブシステムズ株式会社 filed Critical 日立オートモティブシステムズ株式会社
Publication of WO2014097855A1 publication Critical patent/WO2014097855A1/fr

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    • 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
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • 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
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • F16H2001/324—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear comprising two axially spaced, rigidly interconnected, orbital gears

Definitions

  • the present invention relates to a planetary gear mechanism used for a speed reducer and a speed increaser.
  • the planetary gear mechanism is a structure in which the planetary gear is eccentrically arranged with respect to the internal gear, and the eccentricity is canceled by another planetary gear that is similarly arranged eccentrically and having a different number of teeth. It has become.
  • the locus drawn by the tooth surface contact portion of the conventional planetary gear mechanism is not designed to be an epitrochoid curve that rolls with the tooth surface of the planetary gear circumscribing the tooth surface of the internal gear.
  • the locus drawn by the tooth surface contact portion of the planetary gear mechanism is a hypotrochoidal curve in which the pitch circle of the planetary gear rolls while inscribed with respect to the pitch circle of the internal gear.
  • the tooth surface of the planetary gear is circumscribed with respect to the tooth surface of the internal gear and is not designed to have an epitrochoidal curve, the meshing tooth surfaces generate slip.
  • the friction loss of the tooth surface is (Load of tooth surface) ⁇ (Slip distance of tooth surface) ⁇ (Friction coefficient of tooth surface)
  • the slip at the tooth surface contact portion increases the friction loss of the planetary gear mechanism, and the mechanical efficiency deteriorates.
  • the mechanical efficiency of the differential gear mechanism greatly depends on the slip amount of the tooth surface contact portion, and it is an object of the present invention to suppress this slip.
  • the present invention sets S1 smaller than 0.5% of ⁇ D1 when the slip distance S1 of the tooth meshing portion of the internal gear and the planetary gear and the diameter of the pitch circle of the internal gear is ⁇ D1. is there.
  • the friction loss of the tooth surface is It is expressed by (load of tooth surface) ⁇ (slip distance of tooth surface) ⁇ (friction coefficient of tooth surface). Suppression of slip at the tooth surface contact portion reduces friction loss, and mechanical efficiency can be improved.
  • the tooth surface wear is Since it is suppressed by reducing (load of tooth surface) ⁇ (slip speed of tooth surface), wear is reduced and durability is improved by suppressing slip of the tooth surface contact portion.
  • the tooth surface shape for suppressing the slip may be an arc shape or not.
  • the difference in the number of teeth between the internal gear and the planetary gear is 2 or more
  • the diameter of the basic circle that is the center of the teeth of the internal gear is ⁇ C1
  • the diameter of the basic circle that is the center of the teeth of the planetary gear is When ⁇ C2 and the diameter of the pitch circle of the planetary gear are ⁇ D2, the relationship of ⁇ D2 / ⁇ D1> ⁇ C2 / ⁇ C1 is satisfied.
  • the tooth surface friction loss is represented by (tooth surface load) ⁇ (tooth surface slip distance) ⁇ (tooth surface friction coefficient), and suppression of tooth surface contact slip reduces friction loss, Mechanical efficiency can be improved. Further, tooth surface wear is suppressed by reducing (tooth surface load) ⁇ (tooth surface slip speed), so wear is reduced and durability is improved by suppressing slip on the tooth surface contact portion. .
  • the tooth surface shape for suppressing slip may be an arc shape or not an arc shape.
  • the diameter of the base circle that is the center of the teeth of the internal gear A is ⁇ C3
  • the diameter of the pitch circle of the internal gear A is ⁇ D3
  • the diameter of the base circle that is the center of the teeth of the fourth planetary gear is ⁇ C4
  • the relationship when the diameter of the pitch circle of the planetary gear is ⁇ D4 will be described.
  • the difference in the number of teeth between the internal gear A and the planetary gear A is 2 or more, the diameter of the basic circle that is the center of the teeth of the internal gear A is ⁇ C3, and the base that is the center of the teeth of the planetary gear A
  • the diameter of the circle is ⁇ C4 and the diameter of the pitch circle of the planetary gear A is ⁇ D4
  • the relationship of ⁇ D4 / ⁇ D3> ⁇ C4 / ⁇ C3 is satisfied.
  • the planetary gear mechanism operates as a differential gear mechanism, and the downsizing and the large speed reduction that are the features of the differential gear. Ratio or a large speed increase ratio can be realized.
  • the tooth surface of the planetary gear is circumscribed with respect to the tooth surface of the internal gear and is not designed to be an epitrochoid curve, the occurrence of slippage of the meshing tooth surfaces can be suppressed.
  • Sectional drawing of the planetary gear mechanism in the Example of this invention The figure which looked at FIG. 1 in the Example of this invention from the A direction BB sectional view of FIG. 1 in the embodiment of the present invention
  • the enlarged view of the C section of FIG. 2 in the Example of this invention The enlarged view of the D section of FIG. 6 in the Example of this invention.
  • the planetary gear mechanism of this embodiment is used as a reduction gear having a small size and a high gear ratio, and can be applied, for example, as an actuator for parking switching of an automobile.
  • FIG. 1 is a cross-sectional view of a planetary gear mechanism in an embodiment of the present invention
  • FIG. 2 is a view of FIG. 1 in the embodiment of the present invention as viewed from the direction A
  • FIG. Sectional drawing and FIG. 4 are perspective views of the planetary gear mechanism in the embodiment of the present invention.
  • the planetary gear mechanism of this embodiment is used as a reduction gear having a small size and a high gear ratio, and a housing 2 provided with a first internal gear 1 and a bearing (a first rolling to be described later).
  • a second internal gear 3 disposed concentrically with respect to the first internal gear 1 via a bearing 9), a first shaft 4 provided concentrically with the second internal gear 3;
  • a second shaft 6 provided with an eccentric portion 5 rotatably disposed via a bearing (second rolling bearing 10 described later) disposed around the one shaft 4, and a bearing disposed around the eccentric portion 5
  • a second planetary gear 8 provided with a first planetary gear 7 which is rotatably arranged via a third rolling bearing 11 which will be described later.
  • the second shaft 6 When used as a speed reducer, the second shaft 6 is an input shaft, and is rotatably supported by a second rolling bearing 10 disposed around the first shaft 4.
  • the first shaft 4 When used as a speed reducer, the first shaft 4 is an output shaft, and is attached so as to rotate concentrically integrally with the second internal gear 3, and is rotatable with respect to the housing 2 via the first rolling bearing 9.
  • the first planetary gear 7 is rotatably supported by the eccentric portion 5 via the third rolling bearing 11, and is centered on the pitch circle of the first internal gear 1 by the eccentric portion 5. It oscillates and rotates while meshing with the first internal gear 1.
  • the second planetary gear 8 is attached so as to rotate concentrically integrally with the first planetary gear 7, and is arranged so as to be concentrically rotatable with the first internal gear 1. Rotate while meshing.
  • the trochoid curve as a term used in the present embodiment will be described with reference to FIG.
  • a broad trochoidal curve is obtained when a rolling circle rolls around a pitch circle (base circle) without slipping, as shown by a, b, c, a ′, b ′, and c ′ in FIG.
  • This is a locus drawn by a point on the radius of the circle, where the rolling circle is a hypotrochoid that rolls inside the pitch circle (base circle) (a ', b', c '), and the rolling circle is outside the pitch circle (base circle).
  • A, b, c) that rolls are called epitrochoids.
  • hypotrochoid and epitrochoid used in this example refer to the above definitions.
  • the tooth shapes of the internal gear and the planetary gear will be described with reference to FIGS.
  • the tooth surface contact portions of the internal gear 1 and the planetary gear 7 have an arc shape, and the teeth are connected in an arc shape.
  • the difference in the number of teeth between the internal gear and the planetary gear is 2 or more, and the diameter of the basic circle that is the center of the teeth of the internal gear is ⁇ C1,
  • the diameter of the pitch circle of the internal gear is ⁇ D1
  • the diameter of the base circle that is the center of the planetary gear teeth is ⁇ C2,
  • ⁇ D2 / ⁇ D1> ⁇ C2 / ⁇ C1 Satisfying this relationship makes it possible to prevent tooth interference and secure an oil sump space at the tip of the tooth.
  • the number of teeth of the internal gear is N1
  • the number of teeth of the internal gear A is N2
  • the number of planetary gear teeth is N2
  • E When the amount of eccentricity of the planetary gear is E, The tooth surface of the planetary gear moves while rolling with the slip on the tooth surface of the internal gear, and the distance ⁇ S1 that moves while rolling is: E ⁇ (circumference ratio) ⁇ (N1-N2) / N1
  • the diameter ⁇ D1 of the pitch circle of the internal gear is It is represented by E ⁇ N1.
  • E 1.5 mm
  • ⁇ D1 ⁇ 45mm According to the drawing shown in FIG.
  • the distance S1 at which the tooth surface of the planetary gear slips on the tooth surface of the internal gear at this time is 0.02 mm
  • the tooth surface shape shown in FIG. 8 is a modification of the tooth surface shape shown in FIG. 6 and is obtained by removing the tip of the tooth surface that does not contribute to rotation transmission. Can be secured.

Abstract

Selon la présente invention, du fait que la trajectoire tracée par la section de contact de surface de dent d'un mécanisme d'engrenage planétaire ne consiste pas en une courbe épitrochoïde, la perte de frottement augmente et l'efficacité mécanique est réduite en raison du glissement de la section de contact de surface de dent d'une section de transmission de force de rotation. L'efficacité mécanique dudit mécanisme d'engrenage différentiel dépend sensiblement du degré de glissement entre les sections de contact de surface de dent. L'objet de la présente invention est ainsi de limiter ledit glissement. Lorsque la distance de glissement des sections d'engrènement de surface de dent d'un engrenage interne et d'un engrenage planétaire est de (S1) et que le diamètre du cercle primitif de l'engrenage interne est de (φD1), la présente invention établit la distance (S1) de sorte à être inférieure à 0,5 % du diamètre (φD1).
PCT/JP2013/082116 2012-12-21 2013-11-29 Mécanisme d'engrenage planétaire WO2014097855A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012-278822 2012-12-21
JP2012278822A JP2014122668A (ja) 2012-12-21 2012-12-21 遊星歯車機構

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WO2014097855A1 true WO2014097855A1 (fr) 2014-06-26

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WO (1) WO2014097855A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6529863B2 (ja) * 2015-08-28 2019-06-12 住友重機械工業株式会社 偏心揺動型の歯車装置および産業用ロボット
JP7069937B2 (ja) * 2018-03-27 2022-05-18 日本電産トーソク株式会社 電動アクチュエータ
JP7154574B2 (ja) * 2018-10-22 2022-10-18 テクノダイナミックス株式会社 歯車機構、及び、内接式遊星歯車減速機

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61136041A (ja) * 1984-12-03 1986-06-23 Ntn Toyo Bearing Co Ltd トロコイド歯形を用いた減速機
JPH0650394A (ja) * 1992-07-29 1994-02-22 Sumitomo Heavy Ind Ltd 内接噛合遊星歯車構造
JPH11173386A (ja) * 1997-12-11 1999-06-29 Teijin Seiki Co Ltd 遊星歯車装置
JP2010151196A (ja) * 2008-12-24 2010-07-08 Kikuchi Haguruma Kk 減速装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61136041A (ja) * 1984-12-03 1986-06-23 Ntn Toyo Bearing Co Ltd トロコイド歯形を用いた減速機
JPH0650394A (ja) * 1992-07-29 1994-02-22 Sumitomo Heavy Ind Ltd 内接噛合遊星歯車構造
JPH11173386A (ja) * 1997-12-11 1999-06-29 Teijin Seiki Co Ltd 遊星歯車装置
JP2010151196A (ja) * 2008-12-24 2010-07-08 Kikuchi Haguruma Kk 減速装置

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