WO2021248761A1 - Mécanisme de transmission planétaire à roue conique - Google Patents

Mécanisme de transmission planétaire à roue conique Download PDF

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Publication number
WO2021248761A1
WO2021248761A1 PCT/CN2020/120744 CN2020120744W WO2021248761A1 WO 2021248761 A1 WO2021248761 A1 WO 2021248761A1 CN 2020120744 W CN2020120744 W CN 2020120744W WO 2021248761 A1 WO2021248761 A1 WO 2021248761A1
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WIPO (PCT)
Prior art keywords
gear
planetary
tooth profile
curve
sun
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Application number
PCT/CN2020/120744
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English (en)
Chinese (zh)
Inventor
李轩
孙立宁
Original Assignee
苏州大学
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Filing date
Publication date
Application filed by 苏州大学 filed Critical 苏州大学
Publication of WO2021248761A1 publication Critical patent/WO2021248761A1/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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion

Definitions

  • the invention relates to the technical field of gear transmission, in particular to a helical gear planetary transmission mechanism.
  • Gear is a basic component that transmits motion and power through tooth surface meshing.
  • involute gears are widely used because of their convenience in processing and manufacturing, and the separability of center distances.
  • the teeth of involute gears are thin and tall, with poor root bending strength and low tooth surface load-bearing capacity.
  • the number of teeth is at least 17 teeth.
  • the existing involute gear transmission mechanism cannot achieve a large transmission ratio; at the same time, the relative sliding speed between the meshing tooth surfaces near the tooth root near the pitch circle is too high, resulting in this area It is prone to severe wear and can not meet the requirements of high-speed, heavy-duty and high-power gear transmission.
  • the technical problem to be solved by the present invention is to provide a helical gear planetary transmission mechanism, which can improve the tooth root bending strength and tooth surface bearing capacity of the transmission gear, and is not prone to undercutting, and can obtain better results under the same center distance and volume.
  • the large transmission ratio is beneficial to reduce the sliding wear of the gear teeth, which can better meet the requirements of high-speed, heavy-duty, and high-power gear transmission.
  • a helical gear planetary transmission mechanism comprising a sun gear, a planetary gear and an internal gear.
  • the sun gear and the internal gear mesh with the planetary gear.
  • the sun gear, the planetary gear and the internal gear are all helical gears.
  • the normal tooth profile curve of the sun gear is a circular arc curve
  • the normal tooth profile curve of the planetary gear is a cycloid curve
  • the normal tooth profile curve of the internal gear and the cycloid curve are conjugate curves.
  • the cycloid curve is formed by the envelope motion of the circular arc curve, and the normal tooth profile curve of the internal gear is formed by the cycloid curve as the envelope motion.
  • the tooth surface equation of the sun gear is:
  • x 1 , y 1 , z 1 represent the coordinates of the sun gear tooth surface in the x, y and z directions
  • e is the radius of the distribution circle of the sun gear normal tooth profile
  • ⁇ is the arc of the sun gear normal tooth profile
  • Radius n 1 is the number of sun gear teeth
  • k ⁇ 1
  • ⁇ the deflection angle between the center of the arc and the center of the sun gear
  • a is the center distance between the sun gear and the planetary gear
  • n 2 is the number of planetary gear teeth
  • ⁇ is the helix angle
  • the tooth surface equation of the planetary gear is:
  • the tooth surface equation of the internal gear is:
  • x 3 , y 3 , and z 3 represent the coordinates in the x, y, and z directions of the internal gear tooth surface, respectively
  • n 3 is the number of internal gear teeth
  • ⁇ 2 represents the rotation angle of the planetary gear during the formation of the normal tooth profile curve of the internal gear
  • ⁇ 3 represents the rotation angle of the internal gear
  • ⁇ 3 ⁇ [ ⁇ 3o , ⁇ 3t ] is the internal gear tooth profile angle parameter
  • ⁇ 3o is the internal gear tooth profile angle parameter minimum
  • ⁇ 3t is the internal gear tooth profile angle parameter maximum.
  • the number of teeth of the internal gear n 3 n 1 +2n 2 .
  • the sun gear, planetary gears and internal gears all adopt herringbone gears.
  • the present invention has the following beneficial effects:
  • the normal tooth profile curve of the sun gear is a circular arc curve
  • the normal tooth profile curve of the planetary gear is a cycloid curve
  • the normal tooth profile of the internal gear The curve and cycloid curve are conjugate curves, thus forming a conjugate gear pair composed of normal arc, cycloid and cycloid conjugate curve, which realizes spiral meshing transmission.
  • the transmission mechanism has a small slip rate.
  • the minimum number of teeth of the sun gear can reach 1, which can obtain a larger transmission ratio under the same center distance and volume; the gear tooth height of the gear meshing pair is small ,
  • the tooth root is wide, with good tooth root bending strength and tooth surface contact strength, the tooth surface bearing capacity is large and the gear volume is small, which can better meet the transmission requirements of high speed, heavy load and high power.
  • Figure 1 is a schematic diagram of the three-dimensional structure of the helical gear planetary transmission mechanism of the present invention
  • Fig. 2 is a front view of the helical gear planetary transmission mechanism shown in Fig. 1;
  • Fig. 3 is a schematic diagram of the normal tooth profile meshing of the helical gear planetary transmission mechanism shown in Fig. 1;
  • Fig. 4 is a schematic diagram of the formation of the normal tooth profile curve of the sun gear and the planetary gear shown in Fig. 1;
  • Fig. 5 is a schematic diagram of the formation of the normal tooth profile curve of the planetary gear and the internal gear shown in Fig. 1;
  • Fig. 6 is a schematic diagram of the three-dimensional structure of the sun gear shown in Fig. 1;
  • Fig. 7 is a schematic diagram of the three-dimensional structure of the planetary gear shown in Fig. 1;
  • Fig. 8 is a schematic diagram of the three-dimensional structure of the internal gear shown in Fig. 1;
  • Fig. 9 is a structural schematic diagram of the internal meshing helical gear pair composed of planetary gears and internal gears shown in Fig. 1;
  • Fig. 10 is a schematic structural diagram of the external meshing helical gear pair composed of the sun gear and the planetary gear shown in Fig. 1;
  • this embodiment discloses a helical gear planetary transmission mechanism, which includes a sun gear 1, a planet gear 2 and an internal gear 3.
  • the sun gear 1 and the internal gear 3 both mesh with the planet gear 2 in conjugate.
  • the sun gear 1, the planet gear 2 and the internal gear 3 are all helical gears
  • the normal tooth profile curve of the sun gear 1 is a circular arc curve
  • the normal tooth profile curve of the planet gear 2 is a cycloid curve
  • Tooth profile curve and cycloid curve are conjugate curves.
  • the cycloid curve is formed by a circular arc curve doing an enveloping motion
  • the normal tooth profile curve of the internal gear 3 is formed by a cycloid curve doing an enveloping motion.
  • the normal tooth profile curve of the sun gear 1 is a circular arc curve 1a
  • the radius of the circular arc curve 1a is ⁇
  • the production circle (radius ⁇ ) 1b where the circular arc curve 1a is located is based on relative motion
  • the relationship forms an envelope motion to form a cycloid curve 2b
  • the normal tooth profile curve 2a of the planetary gear 2 is a part of the cycloid curve 2b;
  • the cycloid curve 2b performs an envelope motion according to the relative motion relationship to form a conjugate curve 3b, and the normal tooth profile curve 3a of the internal gear 3 is a part of the conjugate curve 3b.
  • the structure of the sun gear 1 is shown in Fig. 6, and the tooth surface equation of the sun gear 1 is:
  • x 1 , y 1 , and z 1 represent the coordinates of the sun gear 1 tooth surface in the x, y, and z directions
  • e is the radius of the distribution circle of the sun gear 1 normal tooth profile
  • ⁇ is the sun gear 1 normal tooth profile
  • n 1 is the number of teeth of sun gear 1
  • ⁇ is the deflection angle of the line connecting the arc center and the sun gear center O
  • a is the center distance between the sun gear 1 and the planetary gear 2
  • ⁇ is the spiral Angle, i 12
  • the helix angle ⁇ of the sun gear 1, the planetary gear 2 and the internal gear 3 are the same, and the gear width B is also the same.
  • the tooth surface equation of the planetary wheel 2 is:
  • x 2 , y 2 , and z 2 represent the coordinates of the tooth surface of the planetary gear 2 in the x, y, and z directions
  • a is the center distance between the sun gear 1 and the planetary gear 2
  • the angle between adjacent gear teeth, ⁇ 1 represents the rotation angle of the sun gear 1
  • ⁇ 2 represents the rotation angle of the planet wheel 2 during the formation of the normal tooth profile curve of the planet gear, that is, when it is made by the arc curve
  • the enveloping motion forms the rotation angle of the planetary wheel 2 in the enveloping motion of the cycloid curve;
  • ⁇ 2 ⁇ [ ⁇ 2o , ⁇ 2t ] is the tooth profile angle parameter of the planetary wheel 2
  • ⁇ 2o is the minimum tooth profile angle parameter of the planetary wheel 2
  • ⁇ 2t is the planetary wheel 2 The maximum value of the tooth profile angle parameter.
  • x 3 , y 3 , and z 3 represent the coordinates in the x, y, and z directions of the tooth surface of the internal gear 3
  • n 3 is the number of teeth of the internal gear 3
  • ⁇ 3 2 ⁇ /n 3 is the adjacent wheel of the internal gear 3
  • the angle between the teeth, ⁇ 3 represents the rotation angle of the internal gear 3
  • ⁇ 2 represents the rotation angle of the planetary gear 2 during the formation of the normal tooth profile curve of the internal gear, which is formed by the enveloping motion of the cycloid curve
  • ⁇ 3 ⁇ [ ⁇ 3o , ⁇ 3t ] is the tooth profile angle parameter of the internal gear 3
  • ⁇ 3o is the minimum tooth profile angle parameter of the internal gear 3
  • ⁇ 3t is the internal gear 3.
  • sun gear 1, planetary gear 2 and internal gear 3 can all adopt herringbone gears, that is, the tooth surfaces of sun gear 1, planetary gear 2 and internal gear 3 can all be designed to be axially symmetrical and spiral.
  • the herringbone structure with the opposite direction can better eliminate the lateral force of the gear on the central axis.
  • the sun gear 1 in the planetary transmission mechanism can also be removed, and the planetary gear 2 and the internal gear 3 can be directly used to form an internal meshing helical gear transmission mechanism.
  • the normal tooth profile curve of the sun gear 1 is a circular arc curve
  • the normal tooth profile curve of the planetary gear 2 is a cycloid curve
  • the normal tooth profile curve and the pendulum curve of the internal gear 3 The line curve is a conjugate curve, thus forming a conjugate gear pair composed of a normal arc, cycloid and cycloid conjugate curve, which realizes spiral meshing transmission.
  • the transmission mechanism has a small slip rate and can effectively avoid The gear fails due to sliding wear; it is not prone to undercutting and is easy to process.
  • the minimum number of teeth of the sun gear can reach 1.
  • the design requirements of small number of teeth and large transmission can be achieved; the gear teeth of this gear meshing pair
  • the tooth height is small, the tooth root is wide, and the modulus is large. It has good tooth root bending strength and tooth surface contact strength.
  • the tooth surface load capacity is large and the gear volume is small, which can better meet high speed, heavy load and high power. Transmission requirements.

Abstract

L'invention divulgue un mécanisme de transmission planétaire à roue conique, comprenant un pignon planétaire (1), un satellite (2) et un engrenage interne (3). Le pignon planétaire (1) et l'engrenage interne (3) sont tous deux engrenés avec le satellite (2) ; le pignon planétaire (1), le satellite (2) et l'engrenage interne (3) sont tous des engrenages coniques ; et une courbe de profil de dent normale du pignon planétaire (1) est une courbe d'arc, une courbe de profil de dent normale du pignon planétaire (2) est une courbe cycloïde, et une courbe de profil de dent normale et une courbe cycloïde de l'engrenage interne (3) sont des courbes conjuguées, de telle sorte que la résistance à la flexion de racine de dent et la capacité de portée de surface de dent d'un engrenage de transmission sont améliorées, la coupe des racines est moins sujette à se produire, un grand rapport de transmission peut être obtenu dans la condition du même entraxe et du même volume, l'abrasion par frottement des dents d'engrenage est considérablement réduite, et les exigences de transmission par engrenages, de vitesse élevée, de charge lourde et de puissance élevée, peuvent être satisfaites avec succès.
PCT/CN2020/120744 2020-06-12 2020-10-14 Mécanisme de transmission planétaire à roue conique WO2021248761A1 (fr)

Applications Claiming Priority (2)

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CN202010536647.1A CN111637200B (zh) 2020-06-12 2020-06-12 一种斜齿轮行星传动机构
CN202010536647.1 2020-06-12

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111637200B (zh) * 2020-06-12 2022-06-14 苏州大学 一种斜齿轮行星传动机构
CN113339460B (zh) * 2021-06-22 2023-04-28 江苏理工学院 渐摆线少齿差行星齿轮副

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100095792A1 (en) * 2007-07-09 2010-04-22 Closed Joint Stock Company "Technology Market" Toothed Wheel Gearing (Variants) and a Planetary Toothed Mechanism Based Thereon (Variants)
CN101936366A (zh) * 2010-09-07 2011-01-05 重庆齿轮箱有限责任公司 一种组合双斜齿行星传动机构
CN202812052U (zh) * 2012-01-13 2013-03-20 河南科技大学 采用齿面修形的斜齿轮行星传动系统
CN105114542A (zh) * 2015-09-01 2015-12-02 重庆大学 一种基于共轭曲线人字齿轮的行星齿轮传动装置
CN106286717A (zh) * 2016-09-14 2017-01-04 大连理工大学 一种对称约束人字齿行星传动装置
CN111637200A (zh) * 2020-06-12 2020-09-08 苏州大学 一种斜齿轮行星传动机构

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107725687A (zh) * 2017-11-07 2018-02-23 江苏万基传动科技有限公司 精密摆线回转关节减速器

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100095792A1 (en) * 2007-07-09 2010-04-22 Closed Joint Stock Company "Technology Market" Toothed Wheel Gearing (Variants) and a Planetary Toothed Mechanism Based Thereon (Variants)
CN101936366A (zh) * 2010-09-07 2011-01-05 重庆齿轮箱有限责任公司 一种组合双斜齿行星传动机构
CN202812052U (zh) * 2012-01-13 2013-03-20 河南科技大学 采用齿面修形的斜齿轮行星传动系统
CN105114542A (zh) * 2015-09-01 2015-12-02 重庆大学 一种基于共轭曲线人字齿轮的行星齿轮传动装置
CN106286717A (zh) * 2016-09-14 2017-01-04 大连理工大学 一种对称约束人字齿行星传动装置
CN111637200A (zh) * 2020-06-12 2020-09-08 苏州大学 一种斜齿轮行星传动机构

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