WO2013040848A1 - 齿条式无级变速器 - Google Patents

齿条式无级变速器 Download PDF

Info

Publication number
WO2013040848A1
WO2013040848A1 PCT/CN2012/001035 CN2012001035W WO2013040848A1 WO 2013040848 A1 WO2013040848 A1 WO 2013040848A1 CN 2012001035 W CN2012001035 W CN 2012001035W WO 2013040848 A1 WO2013040848 A1 WO 2013040848A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
rack
output
drives
shaft
Prior art date
Application number
PCT/CN2012/001035
Other languages
English (en)
French (fr)
Inventor
王录
Original Assignee
Wang Lu
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 Wang Lu filed Critical Wang Lu
Publication of WO2013040848A1 publication Critical patent/WO2013040848A1/zh

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
    • F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
    • F16H29/20—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action the intermittently-acting members being shaped as worms, screws, or racks
    • 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
    • F16H35/00—Gearings or mechanisms with other special functional features
    • F16H2035/003—Gearings comprising pulleys or toothed members of non-circular shape, e.g. elliptical gears

Definitions

  • the utility model relates to a rack-type continuously variable transmission.
  • the existing steel belt type continuously variable transmission cannot transmit large power, and cannot be reversed and reversed.
  • the solution of the present invention is as follows, in view of the disadvantage that the existing steel belt type continuously variable transmission cannot transmit high power and cannot reverse the reverse speed.
  • the technical scheme adopted by the utility model is to convert the shaft rotation into a linear motion, and then convert the linear motion into the shaft rotation. It consists of the following structures: active non-circular gear, driven non-circular gear, axle arm, balance weight, guide groove, double acceleration gear, rack, output gear, output shaft, fixed plate, moving plate, pin, spring, Bevel gears, two cams, hydraulics that control the speed, hydraulics that control steering, rack rods, etc.
  • the active non-circular gear hook speed movement drives the driven non-circular gear to move non-uniformly.
  • the driven non-circular gear drives the shaft arm to move.
  • the bearing at one end of the shaft arm drives the rolling guide block to move in the guiding groove.
  • the guiding groove connects the rack and the rack.
  • Drive the output gear, and the output gear drives the output shaft.
  • Ten holes are evenly distributed on one side of the output gear. In the circumferential direction of the gear, both sides of the hole are inclined by 3 degrees with the gear axis.
  • the output shaft fixed disk is uniformly distributed with nine through holes, and the output shaft moving plate is connected by the key and the output shaft, and nine through holes are uniformly distributed in the disk.
  • the hydraulic device that controls the rotational speed drives the rack tie rod, the rack pull rod drives the double acceleration gear, and the double acceleration gear drives the shaft arm and the balance weight to move along the axis perpendicular to the driven non-circular gear, changing the center of the end of the shaft arm to the slave
  • the distance of the axis of the non-circular gear can be adjusted to adjust the speed ratio.
  • the center end of the shaft arm is on both sides of the driven non-circular gear axis.
  • the hydraulic device that controls the steering controls the different cams to contact the moving plate, and the output gear shaft turns in the opposite direction.
  • the active non-circular gear pitch circle and the driven non-circular gear pitch circle are symmetric with respect to two perpendicular straight lines, so that the active non-circular gear pitch circle, the driven non-circular gear joint circumference length, the instantaneous contact radius, and the instantaneous angular velocity are Ll, L2 , Rl, R2, ⁇ 1, ⁇ 2.
  • the two circles are tangent to the two gear pitch circle lines.
  • the center of the end of the shaft arm is V2 in the direction of the rack, the four arm arms are equally divided by 360 degrees, and each arm is divided by 90 degrees. There is a line of symmetry. , the symmetry line is 45 degrees on each side.
  • the instantaneous angle of the arm is ⁇ .
  • the speed of the arm is changed to COS ( ⁇ /4).
  • the speed of the arm is changed to COS ( ⁇ / ⁇ )
  • the number of arm increases, and the speed changes.
  • Rl* ( l R2* o) 2
  • V2 R2* o 2*C0S ⁇
  • the active non-circular gear pitch circle and the driven non-circular gear pitch circle ensure the axial arm bearing center at the working stroke -45 degrees to + V2 is unchanged at 45 degrees
  • 2*COS 0 is required to be constant
  • the pin and output gear hole joint faces are inclined 3 degrees from the output shaft axis to achieve self-locking.
  • the nine pins and the output gears are evenly distributed on the same circumference. When the pin and the output gear hole are in any position, the pin is in contact with the output gear hole to realize the two-way self-locking.
  • the relationship between the hydraulic device that controls the rotational speed and the hydraulic device that controls the steering is that before the output shaft rotates forward and the center of the end of the shaft arm is located at the axis of the driven non-circular gear shaft, the hydraulic device that controls the steering drives the two cams simultaneously to push the movement.
  • the position of the disc firstly, the hydraulic device that controls the steering drives the two cams, so that the cam that controls the forward rotation is at a position that can push the moving disc, and the cam that controls the reversal moves away from the position that can push the moving disc, and then the hydraulic device that controls the rotational speed is driven.
  • the shaft arm makes the center of the end of the shaft arm deviate from the axis of the driven non-circular gear shaft, so that the output shaft rotates forward.
  • the hydraulic device that controls the speed drives the arm so that the center of the end of the arm is at the axis of the driven non-circular shaft.
  • the hydraulic device that controls the steering drives the two cams at the same time to push the moving disc. Inverting the start and stop processes, the two hydraulic devices change in the same pattern.
  • the utility model has the beneficial effects that high power can be transmitted and the forward and reverse shifting can be performed.
  • Figure 1 is a front view of the guide groove and the rack.
  • Figure 2 is a left side sectional view of the guide groove and the rack.
  • Figure 3 Main view of the rack tie rod
  • Figure 4 is a cross-sectional view of the rack tie rod
  • Fig. 5 is a cross-sectional view of the rack tie rod.
  • Fig. 6 is a curve of the active non-circular gear pitch circle and the driven non-circular gear pitch circle.
  • Fig. 7 is a front view of the fixed disc.
  • Fig. 8 is a sectional view of the fixed disc
  • Figure 9 is a top view of the two cams.
  • Figure 10 is a cross-sectional view of the two cams.
  • Figure 11 is the main view of the pin
  • Figure 12 is the top view of the pin
  • Figure 13 is a cross-sectional view of the screw Figure 14 is a cross-sectional view of the bevel gear
  • Figure 15 is the output gear main view (not drawn) Figure 16 output gear hole sectional view
  • Figure 17 is a front view of the movable plate.
  • Figure 18 is a sectional view of the balance weight.
  • Figure 19 is a front view of the balance weight.
  • Figure 20 is a partial front view of the driven non-circular gear shaft.
  • Figure 21 is a partial plan view of the driven non-circular gear shaft.
  • Figure 22 is a sectional view of the bearing.
  • Figure 23 is a front view of the rolling guide block.
  • Figure 24 is a sectional view of the rolling rail block.
  • Figure 25 is an assembly drawing 1. Hydraulic device for controlling the speed 2. Active non-circular gear 3. Double acceleration gear 4. Axle arm 5. Rolling guide fast
  • the hydraulic device for controlling the rotational speed (1) drives the rack tie rod (17), the rack pull rod drives the double acceleration gear (3), the double acceleration gear drives the shaft arm (4) and the balance weight along the vertical non-circular gear (20) Move in the axial direction, change the distance from the end of the shaft arm to the axis of the driven non-circular gear, and change the speed ratio.
  • the center end bearing (6) is centered on both sides of the driven non-circular gear axis.
  • the hydraulic unit (15) that controls the steering controls the different cams (11) to contact the moving plate (13), and the output shaft (16) is reversed.

Landscapes

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

Abstract

一种齿条式无级变速器，可传递大功率，可正反转变速。该齿条式无级变速器由主动非圆齿轮（2）、从动非圆齿轮（20）、轴臂（4）、导向槽（21）、齿条（7）、输出齿轮（8）、输出轴（16）、销钉（12）、两凸轮（11）、控制转速的液压装置（1）、控制转向的液压装置（15）等构成。主动非圆齿轮（2）匀速运动带动从动非圆齿轮（20）非匀速运动，从动非圆齿轮（20）带动轴臂（4）运动，轴臂（4）一端的轴承（6）带动滚动导轨块（5）在导向槽（21）中运动，导向槽（21）连接齿条（7），齿条（7）带动输出齿轮（8），输出齿轮（8）带动输出轴（16）。主动非圆齿轮（2）的节圆和从动非圆齿轮（20）的节圆保证在工作过程中，轴臂（4）末端轴承（6）的中心沿齿条方向上的速度不变。销钉（12）一端两平面与销钉轴线倾斜3度，与输出齿轮（8）孔配合，实现双向自锁。

Description

齿条式无级变速器
技术领域
本实用新型涉及一种齿条式无级变速器。
背景技术
现有钢带式无级变速器不可传递大的功率， 不可正反转变速。
发明内容
针对现有的钢带式无级变速器不可传递大功率， 不可正反转变速的缺点， 本实用新型的 解决方案如下。
本实用新型采用的技术方案是，将轴转动转变为直线运动，再将直线运动转变为轴转动。 由以下结构构成， 主动非圆齿轮、 从动非圆齿轮、轴臂、平衡配重、 导向槽、双联加速齿轮、 齿条、 输出齿轮、 输出轴、 固定盘、 移动盘、 销钉、 弹簧、 锥齿轮、 两凸轮、 控制转速的液 压装置、 控制转向的液压装置、 齿条拉杆等。
主动非圆齿轮勾速运动带动从动非圆齿轮非匀速运动， 从动非圆齿轮带动轴臂运动， 轴 臂一端的轴承带动滚动导轨块在导向槽中运动， 导向槽连接齿条， 齿条带动输出齿轮， 输出 齿轮带动输出轴。输出齿轮一侧均布十个孔， 在齿轮周向， 孔的两侧面与齿轮轴线倾斜 3度。 输出轴固定盘内均布九个通孔， 输出轴移动盘由键与输出轴连接， 盘内均布九个通孔。 九个 销钉穿过固定盘通孔和移动盘通孔， 一端连接螺丝， 另一端两平面与销钉轴线倾斜 3度， 与 输出齿轮孔配合。 固定盘内弹簧推动销钉与输出齿轮孔接触， 从动非圆齿轮上的锥齿带动锥 齿轮， 锥齿轮带动可在锥齿轮中伸缩的两凸轮转动， 控制转向的液压装置轴向拉动或推动两 凸轮， 转换与移动盘接触的凸轮， 凸轮推动移动盘， 两凸轮与移动盘间也可设置一顶杆， 以 增加销钉动作的灵活性， 移动盘带动销钉与输出齿轮分离。 控制转速的液压装置带动齿条拉 杆， 齿条拉杆带动双联加速齿轮， 双联加速齿轮带动轴臂和平衡配重沿垂直于从动非圆齿轮 轴线方向移动， 改变轴臂末端轴承中心到从动非圆齿轮轴线的距离， 可调节转速比。 轴臂末 端轴承中心在从动非圆齿轮轴线两侧， 控制转向的液压装置控制不同凸轮与移动盘接触， 输 出齿轮轴转向相反。
主动非圆齿轮节圆、 从动非圆齿轮节圆关于两条彼此垂直的直线对称， 令主动非圆齿轮 节圆、 从动非圆齿轮节圆周长、 瞬时接触半径、 瞬时角速度为 Ll、 L2、 Rl、 R2、 ω 1、 ω 2。 两节圆相切于两齿轮节圆连线上， 轴臂末端轴承中心沿齿条方向上的速度为 V2, 四个轴臂平 分 360度， 每个轴臂分得 90度， 存在一对称线， 对称线两侧各 45度。 轴臂瞬时角度为 θ。 轴臂的速度变化为 COS ( π /4), Κ个轴臂时， 轴臂的速度变化为 COS ( π /Κ), 轴臂数增加， 速度变化减小。 因 Rl* ( l= R2* o) 2， V2= R2* o 2*C0S Θ , 主动非圆齿轮节圆、 从动非圆齿轮节圆为保 证轴臂轴承中心在工作行程 -45度到 +45度间 V2不变， 需 2*COS 0为常数， 且主动非圆齿 轮节圆、 从动非圆齿轮节圆保证 Ll= L2, R1加 R2为两齿轮中心距。
销钉与输出齿轮孔接合面与输出轴轴线倾斜 3度， 可实现自锁。 九个销钉与输出齿轮十 个孔均匀位于同一圆周上， 保证销钉与输出齿轮孔在任意位置时， 都有销钉异侧与输出齿轮 孔接触， 实现双向自锁。
控制转速的液压装置与控制转向的液压装置的关系是， 输出轴正转前， 轴臂末端轴承中 心位于从动非圆齿轮轴轴心时，控制转向的液压装置带动两凸轮同时在可推动移动盘的位置， 首先， 控制转向的液压装置带动两凸轮， 使控制正转的凸轮在可推动移动盘的位置， 控制反 转的凸轮离开可推动移动盘的位置， 然后， 控制转速的液压装置带动轴臂， 使轴臂末端轴承 中心偏离从动非圆齿轮轴轴心， 使输出轴正转。 输出轴停转前， 控制转速的液压装置带动轴 臂， 使轴臂末端轴承中心处于从动非圆齿轮轴轴心， 然后控制转向的液压装置带动两凸轮同 时在可推动移动盘的位置。 反转开始与停止过程， 两液压装置变化规律相同。
第一轴臂在 +35度到 +40度时，第二轴臂对应的销钉与齿轮孔接触，第一轴臂在 +40度到 +45度时， 第一轴臂对应的销钉与齿轮孔分离， 四个轴臂依次循环， 确保运动的连续性。
本实用新型的有益效果是， 可传递大功率， 可正反转变速。
附图说明
图 1是导向槽、 齿条主视图 图 2是导向槽、 齿条左视断面图
图 3齿条拉杆主视图 图 4是齿条拉杆断面图
图 5是齿条拉杆断面图 图 6是主动非圆齿轮节圆、从动非圆齿轮节圆的曲线 图 7是固定盘主视图 图 8是固定盘断面图
图 9是两凸轮俯视图 图 10是两凸轮断面图
图 11是销钉主视图 图 12是销钉俯视图
图 13是螺丝断面图 图 14是锥齿轮断面图
图 15是输出齿轮主视图 （未画齿） 图 16输出齿轮孔断面图
图 17是可移盘主视图 图 18是平衡配重断面图
图 19是平衡配重主视图 图 20是从动非圆齿轮轴局部主视图
图 21是从动非圆齿轮轴局部俯视图 图 22是轴承断面图
图 23是滚动导轨块主视图 图 24是滚动导轨块断面图
图 25是装配图 1.控制转速的液压装置 2.主动非圆齿轮 3.双联加速齿轮 4.轴臂 5.滚动导轨快
6.轴承 7.齿条 8.输出齿轮 9.固定盘 10.锥齿轮 11.两凸轮 12.销钉 13. 移动盘
14.螺丝 15.控制转向的液压装置 16.输出轴 17.齿条拉杆 18.弹簧 19.键 20.从动非 圆齿轮 21.导向槽
具体实施方式
控制转速的液压装置（1 )带动齿条拉杆（17)， 齿条拉杆带动双联加速齿轮（3)， 双联 加速齿轮带动轴臂（4)和平衡配重沿垂直于从动非圆齿轮（20)轴线方向上移动， 改变轴臂 末端到从动非圆齿轮轴线的距离， 改变转速比。轴臂末端轴承（6)中心在从动非圆齿轮轴线 两侧， 控制转向的液压装置 (15)控制不同凸轮 (11)与移动盘 (13)接触， 输出轴（16)转向相 反。

Claims

权 利 要 求 书
1. 一种齿条式无级变速器， 由主动非圆齿轮（2)、 从动非圆齿轮（20)、 轴臂 （4)、 平衡配 重、 导向槽（21)、 双联加速齿轮（3)、 齿条（7)、输出齿轮（8)、输出轴（16)、 固定盘
(9)、 移动盘（13)、销钉（12)、 弹簧（18)、锥齿轮（10)、 两凸轮 (11)、 控制转速的液 压装置 (1)、 控制转向的液压装置 (15)、 齿条拉杆 (17)等构成， 其特征是： 主动非圆齿轮 匀速运动带动从动非圆齿轮非匀速运动，从动非圆齿轮带动轴臂运动，轴臂一端的轴承带 动滚动导轨块在导向槽中运动，导向槽连接齿条，齿条带动输出齿轮，输出齿轮带动输出 轴。
2.根据权利要求 1所述的一种齿条式无级变速器， 其特征是： 输出齿轮一側均布十个孔， 在 齿轮周向， 孔的两侧面与齿轮轴线倾斜 3度， 输出轴固定盘内均布九个通孔， 输出轴移动 盘由键与输出轴连接， 盘内均布九个通孔， 九个销钉穿过固定盘通孔和移动盘通孔， 一端 连接嫘丝， 另一端两平面与销钉轴线倾斜 3度， 与输出齿轮孔配合， 九个销钉与输出齿轮 十个孔均勾位于同一圆周上， 保证销钉与输出齿轮孔在任意位置时， 都有销钉异侧与输出 齿轮孔接触， 实现双向自锁。
3.根据权利要求 1所述的一种齿条式无级变速器， 其特征是： 主动非圆齿轮节圆、 从动非 圆齿轮节圆关于两条彼此垂直的直线对称，保证轴臂轴承中心在工作行程间，轴臂末端轴 承中心沿齿条方向上的速度不变。
PCT/CN2012/001035 2011-09-23 2012-08-02 齿条式无级变速器 WO2013040848A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201120378492.X 2011-09-23
CN 201120378492 CN202284634U (zh) 2011-09-23 2011-09-23 齿条式无级变速器

Publications (1)

Publication Number Publication Date
WO2013040848A1 true WO2013040848A1 (zh) 2013-03-28

Family

ID=46296156

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2012/001035 WO2013040848A1 (zh) 2011-09-23 2012-08-02 齿条式无级变速器

Country Status (2)

Country Link
CN (1) CN202284634U (zh)
WO (1) WO2013040848A1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114502859A (zh) * 2020-06-08 2022-05-13 R·R·拉金德兰 具有不间断换挡的伪无级变速器

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN202284634U (zh) * 2011-09-23 2012-06-27 王录 齿条式无级变速器

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1133083A (zh) * 1993-08-30 1996-10-09 艾姆博里治公司 传动机构
DE19528041C1 (de) * 1995-07-31 1997-01-16 Leica Mikroskopie & Syst Fokussiertrieb für den Objekttisch eines Mikroskops
CN1288123A (zh) * 1999-09-15 2001-03-21 刘俊宇 无极变速机构
CN201068967Y (zh) * 2007-07-12 2008-06-04 渠振兴 一种齿啮合无级变速器
CN201461891U (zh) * 2009-07-14 2010-05-12 郑居勇 汽车齿传动无级变速器
CN202284634U (zh) * 2011-09-23 2012-06-27 王录 齿条式无级变速器

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1133083A (zh) * 1993-08-30 1996-10-09 艾姆博里治公司 传动机构
DE19528041C1 (de) * 1995-07-31 1997-01-16 Leica Mikroskopie & Syst Fokussiertrieb für den Objekttisch eines Mikroskops
CN1288123A (zh) * 1999-09-15 2001-03-21 刘俊宇 无极变速机构
CN201068967Y (zh) * 2007-07-12 2008-06-04 渠振兴 一种齿啮合无级变速器
CN201461891U (zh) * 2009-07-14 2010-05-12 郑居勇 汽车齿传动无级变速器
CN202284634U (zh) * 2011-09-23 2012-06-27 王录 齿条式无级变速器

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114502859A (zh) * 2020-06-08 2022-05-13 R·R·拉金德兰 具有不间断换挡的伪无级变速器

Also Published As

Publication number Publication date
CN202284634U (zh) 2012-06-27

Similar Documents

Publication Publication Date Title
CN107345567B (zh) 一种以圆锥螺旋线构造主动线齿的同平面轴线齿轮机构
CN107387704A (zh) 一种同步带单齿条精密传动装置
CN204477279U (zh) 一种机械自动变速箱选换挡执行机构
WO2013040848A1 (zh) 齿条式无级变速器
CN103433922B (zh) 三自由度远心汇交式重载姿态调整机构
CN102808911A (zh) 中空式行星滚柱丝杠副
CN103791055B (zh) 一种汽车无级变速装置
CN110439982B (zh) 一种连杆齿啮式无级变速器
CN202851859U (zh) 中空式行星滚柱丝杠副
CN204985588U (zh) 组合内置式离合器机构的双离合机械变速器
CN109282006B (zh) 同轴脉动式无级变速设备
CN103352965B (zh) 离合式往复平动转化为连续同向旋转运动的机械装置
CN103206522A (zh) 一种减速器用偏心装置
CN110001757B (zh) 基于十字轴万向节的可变速比转向系统
CN203223543U (zh) 一种减速器用偏心装置
CN111677832B (zh) 一种滚压式无级变速器
US1387636A (en) Easy-start driving and reversing mechanism
CN103133615A (zh) 链带式无级变速器
CN105840757A (zh) 一种双减速回转装置
RU2668450C2 (ru) Бесступенчатая коробка передач, установленная со стороны ходового винта для регулирования скорости
CN204127242U (zh) 可变斜面式无级变速器
CN201960069U (zh) 一种用于螺旋压力机飞轮和螺杆连接的结构
CN202251785U (zh) 力矩控制装置
CN104033557A (zh) 一种螺旋滚珠滚道的直线运动减速机构
CN205841662U (zh) 一种双减速回转装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12832903

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 12832903

Country of ref document: EP

Kind code of ref document: A1