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WO2011160590A1 - Coupleur de type engrenage - Google Patents

Coupleur de type engrenage Download PDF

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Publication number
WO2011160590A1
WO2011160590A1 PCT/CN2011/076173 CN2011076173W WO2011160590A1 WO 2011160590 A1 WO2011160590 A1 WO 2011160590A1 CN 2011076173 W CN2011076173 W CN 2011076173W WO 2011160590 A1 WO2011160590 A1 WO 2011160590A1
Authority
WO
WIPO (PCT)
Prior art keywords
epicyclic gear
gear train
stage
gear
train
Prior art date
Application number
PCT/CN2011/076173
Other languages
English (en)
Chinese (zh)
Inventor
孟良吉
Original Assignee
Meng Liangji
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 Meng Liangji filed Critical Meng Liangji
Publication of WO2011160590A1 publication Critical patent/WO2011160590A1/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
    • 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

Definitions

  • the invention belongs to the field of mechanical manufacturing.
  • the present invention generally relates to a mechanism comprised of two epicyclic gear trains that can exhibit flexible transmission characteristics when transmitting design torque.
  • a mechanism comprised of two epicyclic gear trains that can exhibit flexible transmission characteristics when transmitting design torque.
  • the output when applied to automotive technology, when the output is over-speeded due to the vehicle's downhill speed, it exhibits the function of the overrunning clutch that is disconnected from the input end; or, conversely, when the throttle is insufficient to drive, the output is gradually stopped.
  • Overload protection with rotation and input running by itself Specifically, it can be referred to as a gear coupler. Background technique
  • gearboxes As far as road vehicle technology is concerned, there are two main options for gearboxes, namely automatic gearboxes and manual gearboxes.
  • the manual transmission has great application in vehicle technology due to its advantages such as efficiency and cost.
  • a clutch is provided for connecting the power transmission route when combined or cutting off the power transmission route when separating.
  • the clutch is fully integrated with the previous sliding process and can be used to ensure that the vehicle starts slowly. Slip can also be used to protect the parts on the power transmission path from overload.
  • the clutch driven disc is provided with a damping spring in the circumferential direction to isolate the vibration transmission to the transmission to avoid causing bumps between the gears in the transmission.
  • the noise of the abnormal sound and the speed of the car is limited.
  • a double mass flywheel is used to isolate the vibration.
  • the present invention is directed to the above deficiencies of existing clutches, using two different types of epicyclic gear trains, They are butted together to form a flexible geared coupler that can replace the clutch. Since the working angle of the isolated vibration is theoretically unrestricted, it is also superior to the dual mass flywheel technology. In addition, it can also be used in an automatic transmission instead of a torque converter.
  • the present invention relates to a gear type coupler comprising a butted first stage epicyclic gear train and a second stage revolving train wheel train.
  • the two center wheels After the first-stage epicyclic gear train inputs power from the cage, the two center wheels respectively transmit power to one of the cage and the center wheel of the second-stage epicyclic gear train, and the other center wheel of the second-stage epicyclic gear train Output power.
  • One of the first and second stage epicyclic gear trains is a single planetary gear epicyclic gear train and the other is a dual planetary gear epicyclic gear train.
  • the output end of the first stage epicyclic gear train rotates in the same direction
  • second The two inputs of the stage epicyclic gear train are the cage and the inner center wheel. Relatively speaking, such a structure is relatively simple.
  • the first stage epicyclic gear train is a double planetary gear epicyclic gear train and the second stage revolving train wheel is a single planetary gear epicyclic gear train
  • the two input ends of the second stage revolving train wheel are reversely rotated
  • the inner center wheel output of the epicyclic gear train has a one-way turning mechanism so that it can only rotate in the opposite direction relative to its cage. Such a structure can ensure that its output can meet the requirements of the second-stage epicyclic gear train.
  • the first-stage epicyclic gear can be evenly placed outside the other stage in the radial direction, and the axial dimension is further reduced, so that the overall structure is similar to that of the conventional clutches of the prior art.
  • drawings of the present invention are schematic diagrams, all of which omits all bearings, keys and keyways, lubrication methods, bodies, seals, oil drains, etc., which applicants consider to be irrelevant to the description of the technical solution.
  • Detailed structural details In addition to Figure 3, in order to clearly show the meshing relationship between the gears, all the gears are simplified to the outside with the front view of the gears, and the other drawings use the side view of the thickness direction of the gears, the spokes of each gear.
  • the plate is simplified to a line segment, and the gear teeth are simplified to a short line segment at both ends of the web (the oblique short line segment represents the bevel gear); when the gear is idle on the shaft, the line segment is worn on behalf of the shaft It is represented by two parallel short line segments.
  • Figure 1 is a schematic view showing the structure of a conventional single planetary gear epicyclic gear train
  • FIG. 2 is a modified structure commonly used in a conventional planetary gear train
  • FIG. 3 is a schematic structural view of a double planetary gear epicyclic gear train used in the present invention
  • Figure 4 is a schematic view showing the overall configuration of the present invention.
  • Fig. 5 is a schematic view showing another overall configuration of the present invention. detailed description
  • Fig. 1 the two functions of the distribution and synthesis of the epicyclic gear train and the variant of the epicyclic gear train are introduced: as shown in Fig. 1, where 11 is the input gear (and its shaft), 12 is the cage gear, and the web is kept as The frame is equipped with planet gears 14 and 16, 13 and 15 as two center wheels (and their shafts). This is a typical symmetrical turnaround train.
  • the two central wheels 13 and 15 are transmitted according to the rule of equal torque, and it is seen that the train has the function of distributing power. .
  • the two center wheels 13 and 15 are connected to the left and right drive wheels, respectively.
  • the present invention is also referred to as an allocation section.
  • the rotation speed of the cage gear 12 is twice the sum of the rotation speeds of the center wheels 13 and 15.
  • the present invention refers to such an epicyclic gear train as a single planetary gear epicyclic gear train.
  • Another dual planetary gear epicyclic gear train named by the present invention and its function will be described below.
  • the respective shafts are mounted on a cage 33 (the two cages 33 are identical parts of the same cage in the actual configuration), and more outer/inner planetary gear sets may be provided depending on size and needs.
  • This is another complete epicyclic gear train. Compared with the single planetary gear epicyclic gear train shown in Figure 2, it is characterized in that each planetary gear of the single planetary gear epicyclic gear train is connected to the inner and outer center wheel.
  • the outer/inner planetary gears are replaced by two sets of double planetary gear sets.
  • the present invention is referred to as a double planetary gear epicyclic gear train.
  • This double planetary gear epicyclic gear train exhibits a synthetic function, and the power can be combined to the output of the outer sun gear 35.
  • the relationship between the speed and torque vector of the cage of this train and the internal and external sun gear is:
  • Z is the number of teeth
  • R is the rotational speed
  • T is the torque
  • subscript a/b is the outer/inner central gear
  • e is the cage.
  • the overall structure of the gear type coupler of the present invention is as shown in FIG. With the web holder 42 as the boundary, the right half is the first-stage epicyclic gear train responsible for inputting power and distribution.
  • the single planetary gear epicyclic train structure shown in Fig. 2 is used. The names and serial numbers of the parts are the same, but the cancellation is only cancelled.
  • the shaft 22/26 of the two center wheels is replaced by a through shaft 41; the left half is a second stage turning train that is responsible for the combined power and output.
  • the double planetary gear epicyclic gear train shown in Fig. 3, except that the retainer 33 is replaced by a web of the outer center wheel 23, is referred to as a web holder 42, and the shaft 43 of each of the planetary gears is fixedly coupled thereto.
  • the input shaft 27 and the input gear 28 are often omitted, and the cage gear 25 is correspondingly only a disc that connects the engine flywheel, or may be directly the flywheel itself.
  • the inner center wheel 21 and the inner center gear 31 of the second stage double planetary gear epicyclic gear train are directly fixedly connected by the through shaft 41, and the web of the outer center wheel 23 is directly used as the cage of the second stage double planetary gear epicyclic gear train. That is, the web holder 42 directly drives all of the planetary gears 32, 34, 36, 37 on the revolution, so that the power is finally output from the outer sun gear 35.
  • the aforementioned first-stage and second-stage epicyclic gear trains are the same if they are adjusted.
  • the part names following the reference numerals of Fig. 4 are also used, and the unused ones are no longer described by words.
  • the annotation adds an input cage 51, a new through shaft 52 (considering the gear on which the fixed connection is changed), a new web cage 53 (considering a web that is already another gear).
  • the power from the flywheel to the input cage 51 drives the two planetary gear sets 32/34 and 36/37 revolutions, so that the inner center wheel 31 is reversed, the outer center wheel 35 rotates in the same direction, and the power distribution is obtained according to the gear ratio, through the through shaft 52.
  • the web holder 53 of the outer center wheel 35 drives the inner center wheel 21 and the planetary gears 24, 29, so that the power is finally output from the outer sun gear 23.
  • the center wheel 23 carries the load directly, that is, the outer sun gear 35 directly carries the load, then The inner sun gears 31 and 21 are reversely rotated, and the power is combined to the output of the outer center wheel 23.
  • the one-way rotating mechanism has a common mechanism such as a freewheel clutch and a ratchet mechanism, and will not be described in detail by means of the drawings.

Landscapes

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

Abstract

L'invention concerne un coupleur de type engrenage. Le coupleur comprend un train d'engrenages épicycloïdaux de premier degré et un train d'engrenages épicycloïdaux de second degré reliés l'un à l'autre. Après une entrée de puissance par l'appareil, le train d'engrenages épicycloïdaux de premier degré transmet sa puissance à un élément parmi l'appareil et la roue centrale du train d'engrenages épicycloïdaux de second degré par l'intermédiaire de ses deux roues centrales, respectivement, et l'autre roue centrale du train d'engrenages épicycloïdaux de second degré produit la puissance. Un des trains d'engrenages épicycloïdaux de premier degré et second degré est un train d'engrenages épicycloïdaux à simple pignon, tandis que l'autre est un train d'engrenages épicycloïdaux à double pignon. Le coupleur présente une meilleure efficacité et une meilleure performance de traitement qu'un couplage hydrodynamique et un convertisseur de couple. L'angle de travail d'amortissement de torsion du coupleur est plus grand que celui d'un ressort d'amortissement principal ou d'un volant d'inertie à double masse dans un embrayage classique. Dans des conditions normales de fonctionnement, étant donné que toutes les roues planétaires tournent seulement autour de la roue centrale, mais pas autour de leur propre axe, il n'y a pas de différence de vitesse angulaire entre la roue centrale interne et la roue centrale externe, le coupleur fonctionnant ainsi comme un corps rigide. Ainsi, le train d'engrenages épicycloïdaux n'est pas un train d'engrenages épicycloïdaux classique, et présente une meilleure efficacité que ce dernier.
PCT/CN2011/076173 2010-06-24 2011-06-23 Coupleur de type engrenage WO2011160590A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201010217996.3 2010-06-24
CN201010217996.3A CN102297249B (zh) 2010-06-24 2010-06-24 一种齿轮式耦合器

Publications (1)

Publication Number Publication Date
WO2011160590A1 true WO2011160590A1 (fr) 2011-12-29

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2011/076173 WO2011160590A1 (fr) 2010-06-24 2011-06-23 Coupleur de type engrenage

Country Status (2)

Country Link
CN (1) CN102297249B (fr)
WO (1) WO2011160590A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107512310B (zh) * 2017-09-13 2023-12-08 无锡商业职业技术学院 一种基于双级行星齿轮传动的霍尔效应式转向盘角度传感器
CN107499379B (zh) * 2017-09-13 2023-12-01 无锡商业职业技术学院 一种基于双级行星齿轮传动的差动变压器式转向盘角度传感器

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10311386A (ja) * 1997-05-08 1998-11-24 Jatco Corp 自動変速機用歯車変速装置
KR100331639B1 (ko) * 1996-12-13 2002-11-13 현대자동차주식회사 자동변속기용 파워 트레인
CN1696383A (zh) * 2005-06-23 2005-11-16 宁波普尔机电制造有限公司 全自动波轮洗衣机双动力减速离合器
CN101149094A (zh) * 2007-10-25 2008-03-26 同济大学 基于双行星排的混合动力驱动装置
JP2009061923A (ja) * 2007-09-06 2009-03-26 Toyota Motor Corp ハイブリッド車の駆動装置
CN201802824U (zh) * 2010-06-24 2011-04-20 孟良吉 一种齿轮式耦合器

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100331639B1 (ko) * 1996-12-13 2002-11-13 현대자동차주식회사 자동변속기용 파워 트레인
JPH10311386A (ja) * 1997-05-08 1998-11-24 Jatco Corp 自動変速機用歯車変速装置
CN1696383A (zh) * 2005-06-23 2005-11-16 宁波普尔机电制造有限公司 全自动波轮洗衣机双动力减速离合器
JP2009061923A (ja) * 2007-09-06 2009-03-26 Toyota Motor Corp ハイブリッド車の駆動装置
CN101149094A (zh) * 2007-10-25 2008-03-26 同济大学 基于双行星排的混合动力驱动装置
CN201802824U (zh) * 2010-06-24 2011-04-20 孟良吉 一种齿轮式耦合器

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Also Published As

Publication number Publication date
CN102297249A (zh) 2011-12-28
CN102297249B (zh) 2016-03-16

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