WO2008006300A1 - Transmission à roue planétaire à variation continue - Google Patents

Transmission à roue planétaire à variation continue Download PDF

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Publication number
WO2008006300A1
WO2008006300A1 PCT/CN2007/002070 CN2007002070W WO2008006300A1 WO 2008006300 A1 WO2008006300 A1 WO 2008006300A1 CN 2007002070 W CN2007002070 W CN 2007002070W WO 2008006300 A1 WO2008006300 A1 WO 2008006300A1
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WO
WIPO (PCT)
Prior art keywords
transmission
planetary
ratio
gear
main
Prior art date
Application number
PCT/CN2007/002070
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English (en)
Chinese (zh)
Inventor
Qiangguo Xu
Original Assignee
Qiangguo Xu
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 Qiangguo Xu filed Critical Qiangguo Xu
Publication of WO2008006300A1 publication Critical patent/WO2008006300A1/fr

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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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously

Definitions

  • the present invention relates to a mechanical continuously variable transmission in which a planetary gear mechanism is combined.
  • the transmission takes full advantage of the two degrees of freedom of the planetary gear mechanism and actively shifts continuously according to changes in input power and load. It is suitable for variable speed transmission of vehicles and machine tools. ⁇ technology
  • the existing planetary gear shifting mechanism always has one of the three basic components of the brake mechanism, or its movement is subject to certain constraints, so that the mechanism has only one degree of freedom, and transmits power with a certain transmission ratio. The result is only a step-variable shift. In order to achieve stepless speed change, it is used with a torque converter, which makes the structure complicated, the production cost is high, and the transmission efficiency is low.
  • the present invention provides a planetary gear continuously variable transmission.
  • the transmission is a mechanical continuously variable transmission with a combination of planetary gears. It takes full advantage of the two degrees of freedom of the planetary gear mechanism and is capable of active infinitely variable speed depending on changes in input power and load.
  • the planetary gear mechanism consists of three basic components: the sun gear, the ring gear and the planet carrier with planetary gears. There are two basic forms of single planetary row and double planetary row.
  • the single planetary gear mechanism is shown in Fig. 1.
  • the ring gear is internally toothed.
  • the planetary gear is supported on the planet carrier by the axle.
  • the sun gear is at the center, and all the planet gears mesh with the ring gear while meshing with the outer sun gear.
  • the speeds of the three elements of the sun gear, the ring gear and the planet carrier are nl, n2, ⁇ 3, respectively.
  • the number of teeth of the sun gear and the ring gear are zl, ⁇ 2, and the gear ratio of the ring gear and the sun gear is a two z2/zl According to the balance of forces
  • the condition and the law of conservation of energy can derive the characteristic equation of the general motion law of a single planetary gear mechanism:
  • the double planetary gear mechanism is shown in Figure 2:
  • the planet carrier is equipped with inner planetary gears and outer planetary gears, and the ring gear is internally toothed; the inner planetary gear is externally meshed with the sun gear and the outer planetary gear, and the outer planetary gear and the ring gear Engage, the sun gear is at the center.
  • the planetary gear mechanism has two degrees of freedom, whether it is a single planetary row or a double planetary row.
  • the rotational speed of any one component can be continuously changed for any one component; if the rotational speed of the two components is constant, then the rotational speed of the other component is also If the two components can simultaneously change the rotational speed, then the rotational speed of the other component may also be continuously changed, that is, the other component may achieve stepless speed change.
  • the planetary gear continuously variable transmission consists mainly of two planetary rows and a gear ratio control mechanism.
  • the two planets transmit power in two degrees of freedom, one for the main planet and one for the sub-planet. Any two basic elements of the main planetary row are respectively coupled to, or integrated with, the two basic elements of the sub-planetary row, the other element of the main planetary row is the active member, and the other element of the secondary planetary row is driven.
  • the ratio of the speed of the active and the driven parts is the transmission ratio.
  • the transmission ratio control mechanism controls the maximum transmission ratio and the minimum transmission ratio of the transmission, that is, when the control transmission ratio reaches the maximum value, it can be reduced without increasing, and when it reaches the minimum value, it can be increased without further reduction.
  • the gear ratio control method is: one-way locking of a component other than the active member and the driven member, or limiting the range of the rotational speed ratio of two components of the planetary row when the ratio is the maximum value and the minimum value.
  • the power input by the active member and the power output from the driven member are equal in size, that is,
  • M main ⁇ main from "from (2 - 1)
  • M main M is the torque of the active member and the driven member, respectively
  • ⁇ main ⁇ is the angular velocity of the active member and the driven member, respectively.
  • equation (2-1) can be written as:
  • ⁇ main ⁇ is the rotational speed of the active and the follower, respectively.
  • the transmission ratio of the design transmission must be variable, ie the maximum transmission ratio is greater than the minimum transmission ratio and cannot be equal. If they are equal, the transmission can only transmit power with a certain gear ratio, and there is no stepless shifting function. For example, two single planetary rows with the same gear ratio or two double planetary rows with the same gear ratio, any two sets of the same-named components (ie, the sun gear and the sun gear, the ring gear and the ring gear, the planet carrier and the planet carrier) are respectively coupled or made. Integral, another group of the same name as one of the active parts as a follower, the speed of the active and follower is always the same.
  • the technical solution for the one-way single-mode planetary gear continuously variable transmission is to use one main planetary chord and one sub-planetary to transmit power in two degrees of freedom, and the transmission ratio control mechanism to control the maximum transmission ratio of the transmission.
  • Any two elements of the main planetary row are respectively coupled to, or integrated with, two elements of the sub-planetary, the other element of the main planetary row acting as the active part of the transmission, and the other element of the sub-planetary as the transmission
  • the follower, the ratio of the speed of the driving member and the driven member is the transmission ratio of the transmission; the transmission ratio control mechanism can reduce the transmission ratio of the transmission when the driving member is rotated in the working direction without increasing.
  • One-way clutch is used to unidirectionally lock a component other than the active member and the driven member;
  • the beneficial effects of the one-way single-mode planetary gear continuously variable transmission are: compact structure, reliable transmission, and active stepless speed change according to input power and load change; when the active part rotates forward, the follower follows the forward rotation, and the active part is stationary. In this case, the follower can also rotate forward; when the active part is reversed, the transmission idles. It is suitable for bicycles such as bicycles and machines with no power reversal.
  • the technical solution adopted by the one-way dual-system planetary gear continuously variable transmission is: using one main planetary row and one sub-planetary to transmit power with two degrees of freedom and single steering, and controlling the active and driven parts by the speed ratio control mechanism
  • the maximum speed ratio and the minimum speed ratio, the single steering power output from the follower realizes forward and reverse and neutral through the shifting mechanism.
  • Any two elements of the main planetary row are respectively coupled to, or integrated with, two elements of the sub-planetary row, the other element of the main planetary row is the active member, and the other element of the auxiliary planetary row is the driven member;
  • the gear ratio control mechanism controls the speed ratio of the active member and the driven member to no longer increase when the maximum speed ratio reaches the maximum value, and can be increased when the minimum value is reached, and the forward and reverse rotation of the transmission can be realized by the shifting mechanism. files.
  • the shifting mechanism can be used with planetary rows or other gear configurations.
  • One-way clutch is used to unidirectionally lock a component other than the active member and the driven member;
  • the main planetary row and the sub planetary row rotate in two degrees of freedom.
  • the advantages of the one-way dual-system planetary gear continuously variable transmission are: compact structure, reliable transmission, wide speed range (can be designed according to requirements), the transmission can be active between the maximum speed ratio and the minimum speed ratio according to the change of input power and load. Continuously variable speed
  • the technical solution adopted by the two-way single-mode planetary gear continuously variable transmission is:
  • the main planet row and one sub-planetary line transmit power in two degrees of freedom, and the two gear ratio control mechanisms respectively control the maximum gear ratio of the forward and reverse transmissions of the transmission.
  • Any two elements of the main planetary row are respectively coupled to, or integrated with, two elements of the sub-planetary, the other element of the main planetary row acting as the active part of the transmission, and the other element of the sub-planetary as the transmission
  • the follower, the ratio of the speed of the active and the follower is the transmission ratio of the transmission.
  • a gear ratio control mechanism controls the maximum gear ratio of the transmission when the driving member rotates forward, and does not work when the driving member reverses; a gear ratio control mechanism controls the maximum gear ratio of the transmission when the driving member reverses, and the active member does not work when the rotor rotates forward.
  • the two ratio control mechanisms control the steering of the follower to be consistent with the steering of the active member.
  • one-way clutch is used to lock one element except the active part and the driven part, and the working time of the one-way clutch is controlled by the brake;
  • the two-way single-mode planetary gear stepless variable speed output has the advantages of compact structure, reliable transmission, and active stepless speed change according to input power and load change; when the active part rotates forward, the follower follows positive rotation, and the active part reverses. When turning, the follower is reversed. Applicable to machines whose power can be reversed.
  • the technical solution adopted by the two-way dual-system planetary gear continuously variable transmission is: one main planetary platoon and one sub-planetary arranging power are transmitted in two degrees of freedom, and the two transmission ratio control mechanisms respectively control the transmission of the transmission forward and reverse. ratio.
  • Any two elements of the main planetary row are respectively coupled to, or integrated with, two elements of the sub-planetary row, the other component of the main planetary row is the active member, and the other component of the auxiliary planetary row is the driven member.
  • the ratio of the speed of the driving member to the driven member is the transmission ratio of the transmission; a ratio control mechanism controls the maximum transmission ratio and the minimum transmission ratio of the transmission when the driving member rotates forward, that is, the control transmission ratio does not increase when the maximum value is reached.
  • a transmission ratio control mechanism controls the maximum transmission ratio and the minimum transmission ratio of the transmission when the driving member is reversed, that is, the control transmission ratio does not increase when it reaches the maximum value. It can be reduced, it can be increased without reaching the minimum value, and it will not work when the active part is rotating forward.
  • the two ratio control mechanisms control the steering of the follower to be consistent with the steering of the active member.
  • one-way clutch is used to lock one element except the active part and the driven part, and the working time of the one-way clutch is controlled by the brake;
  • FIG. 1 is a block diagram of a single planetary row.
  • Figure 2 is a schematic diagram of the structure of a double planetary row.
  • Figure 3 is a block diagram showing the structure of a first embodiment of a one-way single-mode planetary gear continuously variable transmission.
  • Figure 4 is a block diagram showing the structure of a second embodiment of a one-way single-mode planetary gear continuously variable transmission.
  • Figure 5 is a structure of a preferred embodiment of a one-way dual-system planetary gear continuously variable transmission Schematic diagram, designated as the abstract drawing of the specification.
  • Figure 2 5 sun gear, 6 ring gear, 7 planet carrier, 8 outer planet gears, 9 inner gears.
  • Figure 4 21 main planet row sun gear, 22 main planet gear ring, 23 main planet row planet carrier, 24 planet row sun gear, 25 planet gear ring gear, 26 planet row planet carrier, 27 control maximum transmission Compared to the one-way clutch, 28 input shaft, 29 output shaft.
  • the preferred way to achieve a one-way single-mode planetary gear continuously variable transmission is to use a single planetary row for both the main planetary row and the sub-planetary row, the main planetary sun gear for the active part of the transmission, and the planet carrier or ring gear for the auxiliary planetary row.
  • the two planet rows are mounted on the same axis.
  • the main planet row carrier (12) is integrated with the sub planet row carrier (15), and the main planet gear ring (11) is made up of the outer planet sun gear (13), the main planetary row.
  • the sun gear (10) acts as a transmission active member, directly mounted on the transmission input shaft (19), and the auxiliary planetary gear ring (14) acts as a transmission follower coupled to the output shaft (20);
  • the one-way clutch (16) The race is integrally formed with the planet carrier, and the outer race is coupled to the transmission housing.
  • the gear ratio maximum value i is larger than the gear ratio of the main planetary row a main,
  • the relationship between the number of teeth of the sub-planetary row and the a pair is:
  • the main planetary row carrier (23) is integrated with the sub-planetary sun gear (24), and the main planetary gear ring (22) and the sub-plane gear ring (25) are integrated into one, the main planetary row
  • the sun gear (21) acts as the transmission active member and is mounted directly on the input shaft (28).
  • the sub planet row carrier (26) acts as the transmission follower and the output shaft (29);
  • the one-way clutch (27) The seat ring is integrally formed with the ring gear (22), and the outer race is connected with the transmission housing.
  • the output shaft can be omitted, and the chain is directly attached to the driven member.
  • the preferred way to achieve a one-way dual-mode planetary gear continuously variable transmission is to use a single planetary row for the main planetary chops and the sub-planets, with the main planetary sun gear as the active part of the transmission, and the planet carrier of the sub-planetary as the transmission.
  • the follower, the two planet rows are assembled on the same axis.
  • the main planetary planet carrier (35) is integrated with the sub-planetary sun gear (38); the main planetary row and one sub-planetary share a ring gear (36); the main planetary sun gear (34)
  • the transmission active part it is connected with the input shaft (49); the sub planet row carrier (40) acts as the follower; the one-way clutch (42) inner race and the ring gear (36) are made into one body and the outer race Mounted on the transmission case, one-way locking ring gear (36), controlling the maximum gear ratio;
  • the one-way clutch (43) inner ring is connected with the input shaft (49), the outer race and the main planet carrier ( 35) Together, the speed of the main planet carrier (35) cannot be controlled beyond the input shaft (49) to control the minimum gear ratio.
  • the shifting planetary sun gear (44) is coupled with the follower (40), and is equipped with a forward clutch (47) between the shifting planetary carrier (46); the shifting planetary carrier (46) ) equipped with a reverse brake (48); the shifting planetary gear ring (45) is integrated with the output shaft (50) of the transmission.
  • the clutch (47) is engaged, the brake (48) releases the brake, the shifting planetary gear rotates as a rigid body, and the forward speed is achieved.
  • the ratio of the speed of the active member to the driven member is the transmission ratio of the transmission; the brake (48) brakes the shift.
  • the maximum gear ratio i of the forward gear of the transmission is larger than the gear ratio of the main planetary row a.
  • the sun gear and the planet carrier can be shared with the main planetary row by a planetary train that controls the gear ratio, and the gear ring of the planetary gear is locked in one direction to control the maximum gear ratio of the transmission.
  • the gear ring is locked, the ring gear of the main planetary row is reversed (ie, opposite to the active steering), and the planet carrier of the sub-planetary is rotating forward (ie, the same as the active steering). It is also possible to control the minimum transmission ratio with a planetary row that controls the gear ratio to achieve overspeed.
  • the preferred way to achieve a two-way single-mode planetary gear continuously variable transmission is to use a single planetary row for both the main planetary row and the sub-planetary row, the main planetary sun gear for the active part of the transmission, and the planet carrier for the sub planetary row as the slave for the transmission.
  • the moving parts, the two planetary rows are assembled on the same axis.
  • the main planetary sun gear is used as the active part of the transmission and is connected with the input shaft.
  • the main planetary planet carrier is coupled with the sub-planetary sun gear.
  • the main planetary row and the sub-planetary row share a ring gear, and the sub-planetary row
  • the carrier acts as a follower of the transmission and is integrated with the output shaft.
  • the ring gear acts as the inner race of the two one-way clutches with opposite lock directions.
  • the outer races of the two one-way clutches are respectively controlled by two brakes, that is, the brake lock reverse direction when the active member rotates forward.
  • One-way clutch that locks the forward direction of the clutch to the clutch and reverse rotation.
  • the preferred way to implement a two-way dual-system planetary gear continuously variable transmission is to use a single planetary row for both the main planetary row and the sub-planetary row, the main planetary sun gear for the active part of the transmission, and the planet carrier for the sub planetary row as the slave for the transmission.
  • the main planetary sun gear is used as the active part of the transmission and is connected with the input shaft.
  • the main planetary planet carrier is coupled with the sub-planetary sun gear.
  • the main planetary row and one sub-planetary share a ring gear.
  • the planet carrier acts as a follower of the transmission and is integrated with the output shaft of the transmission.
  • the ring gear acts as the inner race of the two one-way clutches with opposite lock directions.
  • the outer races of the two one-way clutches are respectively controlled by two brakes, that is, the brake lock reverse direction when the active member rotates forward.
  • One-way clutch that locks the forward direction of the clutch to the clutch and reverse rotation.
  • the rotation speed of the main planet carrier in the forward rotation and the reverse rotation of the driving member cannot exceed the input shaft, and the outer races of the two one-way clutches are connected with the main planet carrier.
  • the inner race is connected to the input shaft via two clutches.
  • the minimum transmission ratio of the two-way two-way planetary gear continuously variable transmission is equal to one.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Structure Of Transmissions (AREA)

Abstract

Une transmission par engrenages à roue planétaire à variation continue est une transmission mécanique à roue planétaire à variation continue composée de trains planétaires. Cette transmission utilise pleinement deux degrés de liberté des trains planétaires pour modifier le déplacement à l'infini. Elle comprend principalement deux trains planétaires et un mécanisme de commande du rapport de transmission. Ces deux trains planétaires peuvent transmettre la puissance avec deux degrés de liberté, un train constituant le train planétaire principal et l'autre train constituant le train planétaire auxiliaire. Les deux éléments basiques (35, 36) du train planétaire principal peuvent se coupler à, venir en contact avec ou être formés d'une seule pièce composée des deux éléments basiques (38, 36) du train planétaire auxiliaire. Un autre élément (34) du train planétaire principal sert d'élément d'entraînement de transmission, un autre élément (40) du train planétaire auxiliaire sert d'élément d'entraînement. Le mécanisme de commande du rapport d'engrenage peut commander le rapport de vitesse maximal et le rapport de vitesse minimal entre l'élément d'entraînement et l'élément entraîné, c.a-d. que le rapport de vitesse n'augmente pas lorsque la valeur minimale est atteinte et ne diminue pas lorsque la valeur minimale est atteinte. Cette transmission est de structure compacte, a un fonctionnement fiable et dispose d'une large plage de transmission. Elle peut transmettre par variation continue positive entre le rapport de vitesse maximal et le rapport de vitesse minimal en fonction de la modification de la puissance d'entrée et de la charge de sortie.
PCT/CN2007/002070 2006-07-05 2007-07-04 Transmission à roue planétaire à variation continue WO2008006300A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CNA2006100909467A CN1959147A (zh) 2006-07-05 2006-07-05 行星齿轮无级变速器
CN200610090946.7 2006-07-05

Publications (1)

Publication Number Publication Date
WO2008006300A1 true WO2008006300A1 (fr) 2008-01-17

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WO (1) WO2008006300A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101571182A (zh) * 2008-04-30 2009-11-04 陈解生 有级变速器
CN104100682A (zh) * 2013-04-11 2014-10-15 孟良吉 扭矩匹配自锁错位对接的齿轮式耦合器
CN111556937A (zh) * 2018-05-28 2020-08-18 罗灿 同向分动差速传动器

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102022508B (zh) * 2009-09-09 2014-06-04 吴志强 一种复合型向心式液力变矩器
JP2012002353A (ja) * 2010-05-19 2012-01-05 Jatco Ltd 変速機のパーキング機構
CN102359559A (zh) * 2011-09-28 2012-02-22 安徽农业大学 一种数控机械式自动变速器
CN103438164B (zh) * 2013-07-27 2015-12-23 顺德职业技术学院 一种多速变速器传动机构
CN104728367A (zh) * 2015-01-15 2015-06-24 杨晋杰 一种前驱轿车用无级变速器
IT201600071646A1 (it) * 2016-07-08 2018-01-08 Nuovo Pignone Tecnologie Srl Trasmissione a velocita' variabile e sistema che la utilizza
CN107269782A (zh) * 2017-08-08 2017-10-20 邓进桃 机械齿轮式无级自动变速器
CN108412982B (zh) * 2018-05-11 2024-01-26 中国人民解放军陆军军事交通学院 一种组合式非圆齿轮无级变速传动装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS56131855A (en) * 1980-03-16 1981-10-15 Riichi Tomoyose Stepless speed changer utilizing planetary gear
FR2540209A1 (fr) * 1983-01-28 1984-08-03 Soma Europ Transmissions Transmission a engrenages, en particulier pour turbine a arbre libre
JPH11247950A (ja) * 1998-02-27 1999-09-14 Hochiki Corp 減速装置
CN1598356A (zh) * 2004-09-09 2005-03-23 姚保民 行星齿轮无级变速装置
CN2758560Y (zh) * 2004-03-19 2006-02-15 刘磊 一种齿轮无级变速器

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS56131855A (en) * 1980-03-16 1981-10-15 Riichi Tomoyose Stepless speed changer utilizing planetary gear
FR2540209A1 (fr) * 1983-01-28 1984-08-03 Soma Europ Transmissions Transmission a engrenages, en particulier pour turbine a arbre libre
JPH11247950A (ja) * 1998-02-27 1999-09-14 Hochiki Corp 減速装置
CN2758560Y (zh) * 2004-03-19 2006-02-15 刘磊 一种齿轮无级变速器
CN1598356A (zh) * 2004-09-09 2005-03-23 姚保民 行星齿轮无级变速装置

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101571182A (zh) * 2008-04-30 2009-11-04 陈解生 有级变速器
CN104100682A (zh) * 2013-04-11 2014-10-15 孟良吉 扭矩匹配自锁错位对接的齿轮式耦合器
CN111556937A (zh) * 2018-05-28 2020-08-18 罗灿 同向分动差速传动器
CN111556937B (zh) * 2018-05-28 2022-09-23 罗灿 同向分动差速传动器

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