WO2012019318A1 - 齿啮合传动无级变速器 - Google Patents

齿啮合传动无级变速器 Download PDF

Info

Publication number
WO2012019318A1
WO2012019318A1 PCT/CN2010/001217 CN2010001217W WO2012019318A1 WO 2012019318 A1 WO2012019318 A1 WO 2012019318A1 CN 2010001217 W CN2010001217 W CN 2010001217W WO 2012019318 A1 WO2012019318 A1 WO 2012019318A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
tooth
shaft
groove plate
arc groove
Prior art date
Application number
PCT/CN2010/001217
Other languages
English (en)
French (fr)
Inventor
金哲根
Original Assignee
Jin Zhegen
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 Jin Zhegen filed Critical Jin Zhegen
Priority to PCT/CN2010/001217 priority Critical patent/WO2012019318A1/zh
Publication of WO2012019318A1 publication Critical patent/WO2012019318A1/zh

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H9/00Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/02Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
    • F16H9/24Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using chains or toothed belts, belts in the form of links; Chains or belts specially adapted to such gearing
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H55/00Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32Friction members
    • F16H55/52Pulleys or friction discs of adjustable construction
    • F16H55/54Pulleys or friction discs of adjustable construction of which the bearing parts are radially adjustable

Definitions

  • the present invention relates to a mechanical continuously variable transmission.
  • CVT continuously variable transmissions
  • the invention provides a gear meshing transmission infinitely variable transmission technology, wherein the speed ratio converter of the stepless speed changer is the same.
  • the so-called shrinking gear is a linear trough with four or more linear grooves on the two discs fixed on the rotating shaft.
  • the movable teeth are the teeth and the tooth arm.
  • the wrist and the tooth are composed, wherein the tooth arm moves back and forth in the straight groove so that the diameter of the entire tooth composed of the movable teeth with the same number of slots is simultaneously, the same length, increases or decreases, and the movement of the tooth arm is the tooth wrist
  • the arc trough is caused by the movement of the arc groove.
  • the two arc grooves on the outer two sides of the two linear troughs can rotate at the same angle and at the same angle. Each of them has a straight line on the linear trough.
  • the same number and the same angle of the arc groove of the groove When the angle of the arc groove is rotated, the movement of the tooth in the arc groove causes the connected tooth arms to move in the linear groove to increase or decrease the diameter of the entire tooth.
  • Such a gear is called a shrinking gear, and a pair of increasing and contracting gears and a toothed chain or a roller chain meshing transmission become a speed ratio converter.
  • the gear mesh transmission stepless transmission adopting the above technology has significant advantages, namely, no variable speed noise, large transmission torque, no slip phenomenon, good speed average speed, large starting torque, small mechanical wear, small variable speed power consumption, and can be used with teeth.
  • the chain or roller chain meshes the transmission. When the high power is transmitted, the modulus of the gear teeth and the chain teeth is selected. When the roller chain is used, multiple rows of chains can be used. If more power is transmitted, more than one pair of gear reduction pairs When used in parallel, to increase the shift range, increase the diameter of the shrink-retracting gear or use one or more pairs of tightening gears in series.
  • Figure 1 shows the meshing diagram of the contraction gear and the toothed chain in the toothed transmission continuously variable transmission of the present invention.
  • Figure 4 is a perspective view of the linear grooved disk and the curved grooved disk
  • Figure 5 Stereo view of arc slot and linear slot
  • Figure 6 is a cross-sectional view of the same axis type tooth meshing transmission continuously variable transmission of the input shaft output shaft of the present invention.
  • Fig. 7 is a schematic view of the parallel shaft type tooth meshing transmission stepless transmission of the present invention
  • the active and driven contraction gear mounting structure is the hub 17 of the linear groove plate 21 on the shaft 13 with a screw 20 or Fixed by key installation, another similar linear groove plate is fixedly mounted on the corresponding surface, and there are circular protrusions on the outer surface of the disk.
  • the two linear groove plates are symmetrically arranged with four or more equally distributed linear grooves. 18, the length is the gear ratio is large, the hour is short, the tooth arm 33 of the movable tooth 30 and the other side arm are placed on the two linear grooves, and the two arc grooves of the arc groove plate 21 are arranged on the outer sides of the linear groove plate
  • the number and distribution angle of the arc groove 22 of the disk are the same as the number and angle of the linear groove of the linear groove disk.
  • the length of the arc groove is made up of the maximum point of the linear groove and the longest arc groove connected at the minimum.
  • the toothed arm 34 of the movable tooth 30 is placed in the arc groove, and the other side of the toothed wrist 34 is also disposed in the opposite arc groove.
  • the ring gear 25 fixedly mounted on the arc groove plate is meshed by the planetary gear 24,
  • the planetary gears are equally distributed on one side with two or more sides.
  • the planetary gears are connected to the other side of the planetary gears via the shaft 23.
  • the planetary gears mesh with the fixedly mounted ring gears on the other side of the arc grooved disk.
  • the arc slot on the other side of any one of the arc slots Rotating, toothed arc groove hold the movable arm rotating movement causes the toothed gear diameter reduced by the linear change in the slot, the rotational speed of the disc groove the arc determines the gear speed.
  • the planetary gear cover 27 is fixedly mounted on the arc groove plate, the cover 27 contacts the shaft through the ball 28, and the ball is filled on the inner diameter of the cover.
  • the inner side of the arc groove plate has a circular protrusion and is sleeved on the outer side of the linear groove plate.
  • the part makes the arc groove plate rotate stably, the power is the rotation of the motor or the hydraulic cylinder, the rotation of the hub motor 68 can be used to drive the gear 69, the intermediate gear 70 rotates the intermediate gear shaft to connect the worm gear 71 and the meshed worm wheel shaft is mounted with the bevel gear 72, the gear 72 The arcuate bevel rack 26 fixedly mounted on the arc chute is engaged with the transmission arc chute.
  • Another method is that the oil pressure is rotated, that is, the high-pressure oil enters the shaft through the straight-type rotary valve 66, and the hydraulic cylinder 65 pushes the angular rotation of the arc groove plate through the piston lever, and the two expansion and contraction gears are required regardless of the motor or the hydraulic cylinder. Synchronous increase or decrease in the same distance.
  • the movable teeth 30 on the linear groove plate can be used with herringbone or helical teeth, but the helix angle should not be too large.
  • One tooth 30 or two teeth 37 or more teeth can be used. A plurality of different numbers of teeth are used in combination, and the volume of the grooved disk is correspondingly increased after the number of teeth is increased.
  • the roller 35 is sleeved on the outer diameter of the toothed arm 34, and the roller is rolled in the arc groove to reduce friction during movement.
  • the movable tooth upper flap 36 prevents the toothed chain or the roller chain from directly contacting the linear groove plate to generate wear and noise. If the rotational speed of the toothed chain 6 is high, the intermittent toothed chain 39 can be used with a full toothed chain 40 when the rotational speed is low.
  • the tooth tips of the movable tooth and the toothed chain are to be trimmed into a triangle and the teeth are to be machined with a negative displacement tooth.
  • the pitch can be adjusted to be larger or smaller so that the movable tooth and the toothed chain have sufficient clearance, if a roller chain is used.
  • the roller diameter of the roller chain of the full roller chain 49 can be smaller than the standard, and the teeth should also be processed with negative displacement teeth so that the teeth and the roller chain have a large gap, and the movable teeth of the roller chain can be used with one tooth 50. Or more than one series of teeth 57 or parallel teeth 58 and the like. If the torque is large, you can use multiple rows of chains.
  • the above toothed chain or roller chain meshes with the shrinking gear When the gear speed is increased at a high speed, the speed of the teeth increases. When the moving speed of the toothed chain is fast, it is possible to get stuck with each other.
  • the gears 99 and 101 are mounted on the gear holder 97, and its function is to lift the tooth profile.
  • the chain or roller chain has to be meshed with the pinching gear so that it does not get stuck. Its other function is to tighten the toothed chain or the roller chain by the springs 98 and 100.
  • the speed of the gear is increased and the speed of the gear is not high.
  • the expansion gears can be directly mounted with intermittent or intermittent roller chains.
  • the above-mentioned contraction gear and toothed chain meshing technology can manufacture a parallel shaft type tooth meshing continuously variable transmission and the same axis type tooth meshing rotary continuously variable transmission having the same line of input and output axes.
  • the parallel shaft type transmission input shaft 1 and output shaft 15 are parallel, the rotation of the prime mover is rotated by the clutch 3 to actively expand and contract the gear 4, and the gear and the toothed chain 6 mesh with the rotary driven reduction gear 5
  • the expansion and contraction gears are each increased and contracted to complete the shifting.
  • the transmission forward and reverse shifting gears are the sun gear 7 and the planetary gear 8, which are connected to the shaft 14, the ring gear 9, the planetary carrier 10, the reverse brake 11, and the forward gear.
  • the clutch 12, the combined positive and negative shifting gears, and the forward and reverse shifting technology are not mentioned in the known technology.
  • the above-mentioned positive and negative shifting gears are mounted on the output shaft. If the retracting gears are frequently reversed and reversed when the input shaft is mounted, the sudden change of the speed of the toothed chain and the roller chain causes a series of adverse effects, so The reverse shift gear train is mounted on the output shaft.
  • the input axis and the output axis are the same axis gear meshing transmission.
  • the continuously variable transmission is an input shaft 59 on which the input pinion 61 is mounted, the gear meshes with the input pinion 63, and the gear is an active pinch gear shaft 13 which is fixedly mounted on the shaft 13
  • the rotation of the fixedly mounted active reduction gear 4 causes the toothed chain 6 to drive the driven expansion and contraction gear 5 to rotate its two expansion and contraction gears to form a speed ratio converter
  • the driven expansion and contraction gear is a shaft 14 with a key or a screw 20
  • the end of the shaft 14 is fixedly mounted on both sides of the output large gear 74, and the forward-rotation output pinion 75 and the reverse output pinion 86 which are normally meshed and rotated are respectively mounted.
  • the coaxial positive and negative shifting gears are forward-rotating output pinions 75.
  • the hollow shafts 76 mounted on one side of the output shaft 96 are in contact with the outer diameter balls 78, and the balls 78 are filled with the outer diameter of the hollow shafts.
  • One side of the ball is an outer diameter ball retaining ring 79, and the other side is a brake drum 80 fixedly mounted on the forward output pinion 75 to position the gear on the hollow shaft, and the inner diameter of the hollow shaft is placed on both sides.
  • the ball 77 is in contact with the output shaft 96.
  • the ball 77 is filled with the inner diameter of the hollow shaft.
  • the ball side is the output shaft shoulder, and the other side is the sleeve 102 to position the hollow shaft on the output shaft.
  • the sleeve 102 It is a screw 103 that is fixedly mounted on the shaft.
  • the outer diameter of the brake drum 80 has a brake belt 81 fixedly mounted on the output shaft.
  • the belt is a hydraulic cylinder 82 and a piston lever to tighten, and the gear is braked.
  • the high pressure oil of the hydraulic cylinder 82 is a straight-through rotary valve 83, and the reverse output small gear 86 is an outer diameter ball 89 on both sides of the hollow shaft 87 mounted on the other side of the output shaft 96.
  • the ball 89 is a hollow shaft. The outer diameter of the ball is filled, and the ball 89 is fixed to the gear 86.
  • the brake drum 92 is mounted, and the outer side is an outer diameter ball retaining ring 90 for positioning the gear 86 on the hollow shaft.
  • the balls 88 are in contact with the output shaft 96, and the balls 88 are in the inner diameter of the hollow shaft.
  • the upper part is the output shaft shoulder, and the other side is the sleeve 104 to position the hollow shaft on the output shaft 96.
  • the sleeve 104 is a screw 105 for fixed mounting on the shaft.
  • the brake band 93 is mounted on the outer diameter of the brake drum 92, and the belt is fixedly mounted on the output shaft 96.
  • the belt 93 is tightened by the hydraulic cylinder 94 and the piston lever and the control gear 86 is braked, and the output shaft 96 is reversed. Turn, loose time slots.
  • the high-pressure oil is a right-angle rotary valve 85 into the hydraulic cylinder 94.
  • the output large gear 74 brakes When the above-mentioned forward and reverse brakes are tight, the output large gear 74 brakes, the output shaft 96 is loose when the brakes are loose, and the band brake can also use the multi-plate brake.
  • a controllable one-way overrunning clutch instead, the pull of the overrunning clutch puller is pulled by the hydraulic cylinder and the piston lever.
  • the positive and negative gears are suspended in the opposite direction on the same axis, which do not affect each other and the relative speed on the shaft is not high. If there is no hollow shaft, only the balls or the bearings are rotated twice as high as each other, and the wear and tear of the parts is large and the noise is large.
  • coaxial positive and negative shifting gear trains have the advantages of smaller volume, fewer gears, and simpler than the planetary gears.
  • the above-mentioned invention solves many shortcomings of the friction type continuously variable transmission and realizes a true gearless transmission with a tooth and tooth meshing transmission, which has large turning torque, small volume, simple structure, and can be used in small and large vehicles or Large and small machinery on a fixed location.

Landscapes

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

Description

说 明 书
齿啮合传动无级变速器
技术领域- 本发明涉及一种机械式无级变速装置。
背景技术- 现在的机械式无极变速器(CVT)是摩擦式、 链式、 带式等。 都是接触处产生 摩擦力进行传动因此它有许多缺点。 用在机动车上时链或带在链轮上打滑因此 效率低、 传动扭矩小, 要传动大扭矩必须增大链和轮的摩擦力使更多的功在摩 擦中消耗使功耗增加, 有时停车后再起步难、 变速时噪声大、 传动不稳定、 带 的寿命短, 因此 CVT变速器现在只用在小型车上。
发明内容- 上述 CVT变速器诸多的缺点是因为摩擦传动扭矩造成的, 因此根本上改变这 种缺点的技术是齿啮合传动。 本发明提供齿啮合传动无极变速技术, 其无极变 速器的速比变换器是一样的两个增缩齿轮中一个齿轮直径增大时另一个齿轮直 径缩小, 经齿形链啮合传递动力实现无极变速。 所谓增缩齿轮是转轴上固定的 一样的两个圆盘上有对应的 4个或 4个以上直线槽的直线槽盘, 其槽里按放活 动齿, 其活动齿是齿身、 齿臂、 齿腕和齿组成, 其中齿臂在直槽里来回移动使 跟槽数一样的活动齿组成的整个轮齿的直径同时、 同长、 增大或缩小, 其齿臂 的移动是齿腕在弧线槽里移动造成的, 其弧线槽盘是两个直线槽盘外两侧轴上 可以同时、 同角度旋转的两个一样的弧线槽盘, 其上各有直线槽盘上的直线槽 对应的同数、 同角度的弧线槽, 在弧线槽盘角度旋转时弧线槽里的齿腕移动使 连在一起的齿臂在直线槽里移动使整个轮齿直径增大或缩小, 这样的齿轮叫增 縮齿轮, 其一增一缩的一对增缩齿轮和齿形链或滚子链啮合传动就成了速比变 换器。
采用上述技术的齿啮合传动无极变速器有显著的优点, 即无变速噪声、 传动 扭矩大、 没有打滑现象、 变速均速性好、 起步力矩大、 机械性磨损小、 变速功 耗小、 可以用齿形链或滚子链啮合传动, 要传递大功率时轮齿和链齿的模数选 大, 用滚子链时可以用多排链, 如果传递更大功率时一对以上的增缩齿轮对并 联使用, 要扩大变速范围时要增加增缩齿轮的直径或一对以上的增缩齿轮对串 联使用。 附图说明
图 1 本发明的齿啮合传动无级变速器中增缩齿轮和齿形链啮合图
图 2 直线槽盘剖视图
图 3 弧线槽盘剖视图
图 4 直线槽盘和弧线槽盘立体图
图 5 弧线槽盘和直线槽盘立体图
图 6 本发明的输入轴线输出轴线同一轴线式齿啮合传动无级变速器剖视图 图 7 本发明的平行轴式齿啮合传动无极变速器简图
1齿轮、 2输入轴、 3离合器、 4主动增缩齿轮、 5从动增缩齿轮、 6齿形链、 7太阳齿轮、 8行星齿轮、 9齿圈、 10行星齿轮架、 11倒档制动器、 12前进档 离合器、 13主动增缩齿轮轴、 14从动增缩齿轮轴、 15输出轴、 16直线槽盘、 17直线槽盘轮毂、 18直线槽、 19行星齿轮轴孔、 20轮毂固定用螺丝、 21弧线 槽盘、 22弧线槽、 23行星齿轮轴、 24行星齿轮、 25齿圈、 26弧形锥齿条、 27 行星齿轮盖、 28滚珠、 29滚珠压板、 30—个齿的活动齿、 31齿、 32齿身、 33 齿臂、 34齿腕、 35滚筒、 36挡片、 37两个齿的活动齿、 38三个齿的活动齿、 39间歇齿形链、 40满齿形链、 41齿、 42外链板、 43内链板、 44轴、 45间歇滚 子链、 46滚筒、 47外链板、 48内链板、 49满滚子链、 50链轮活动齿、 51齿、 52齿身、 53齿臂、 54齿腕、 55滚筒、 56挡片、 57两齿串联齿、 58两齿并联齿、 59输入轴、 60轴承、 61输入小齿轮、 62轴承、 63输入大齿轮、 64轴承、 65液 压缸、 66直通式旋转阀、 67轴承、 68轮毂电机、 69电机齿轮、 70中间齿轮、 71蜗杆齿轮、 72蜗轮轴连接的锥齿轮、 73轴承、 74输出大齿轮、 75正转输出 小齿轮、 76空心轴、 77空心轴内径滚珠、 78空心轴外径滚珠、 79外径滚珠挡 圈、 80制动鼓、 81制动带、 82液压缸、 83直通式旋转阀、 84高压油管、 85直 角式旋转阔、 86反转输出小齿轮、 87空心轴、 88空心轴内径滚珠、 89空心轴 外径滚珠、 90外径滚珠挡圈、 91制动鼓固定用螺丝、 92制动鼓、 93制动带、 94液压缸、 95轴承、 96输出轴、 97齿轮固定架、 98弹簧、 99齿轮、 100弹簧、 101齿轮、 102轴套、 103轴套固定用螺丝、 104轴套、 105轴套固定用螺丝。 下面结合附图对本发明的一种实施方式做进一步的描述:
主动、 从动增缩齿轮安装结构是轴 13上直线槽盘 21的轮毂 17用螺丝 20或 用键固定安装, 对应面上固定安装另一个一样的直线槽盘, 盘外面上各有圆形 突起部, 两个直线槽盘上对称的各有 4个或 4个以上的均等分布的直线槽 18, 长度是变速比大时长、 小时短, 两盘直线槽上安放活动齿 30的齿臂 33和另一 侧齿臂, 直线槽盘外两侧各安装弧线槽盘 21两个弧线槽盘的弧线槽 22的数和 分布角度是跟直线槽盘的直线槽的数和角度一样, 弧线槽的长度是直线槽的最 大点和最小处连接的最长的弧线槽做成的, 弧线槽中安放活动齿 30的齿腕 34, 对面的弧线槽里也对应安放齿腕 34的另一侧齿腕, 弧线槽盘上固定安装的齿圈 25是行星齿轮 24啮合, 行星齿轮是一侧面上有两个或两个以上的均等分布的, 行星齿轮通过轴 23连接另一侧行星齿轮, 行星齿轮与另一侧弧线槽盘上固定安 装的齿圈啮合使两侧弧线槽盘中任意一个转动时另一侧的弧线槽盘也旋转, 弧 线槽托起齿腕旋转使活动齿在直线槽里移动使增缩齿轮直径的变化, 弧线槽盘 的旋转速度决定变速速度。 行星齿轮盖 27是固定安装在弧线槽盘上, 盖 27通 过滚珠 28接触轴, 滚珠是装满盖内径上, 弧线槽盘内侧有圆形突起部套上了直 线槽盘外侧上的突起部使弧线槽盘稳定的旋转, 动力是电机或液压缸转动, 可 用轮毂电机 68旋转带动齿轮 69中间齿轮 70旋转中间齿轮轴连接蜗杆齿轮 71 和啮合的蜗轮轴上安装锥齿轮 72,齿轮 72和弧线槽盘上固定安装的弧形锥齿条 26啮合传动弧线槽盘。
另一种方法是油压来转动的即高压油经直通式旋转阀 66进入轴后进液压缸 65 通过活塞杠杆推动弧槽盘角度旋转, 无论釆用电机或液压缸都要使两个增缩齿 轮同步同距增大或缩小, 直线槽盘上的活动齿 30是可以用人字齿或斜齿可是其 螺旋角不要过大, 可以用一个齿 30或两个齿 37或两个以上齿, 还可以用多个 不同的个数齿混合使用, 齿数多后槽盘的体积也要相应的增加, 滚筒 35是齿腕 34外径上套上的, 滚筒在弧线槽里滚动旋转使移动时减少摩擦力, 活动齿上挡 片 36是防止齿链或滚子链直接接触直线槽盘产生磨损和噪声, 齿形链 6如果转 速高时用间歇齿形链 39转速低时可以用满齿形链 40,活动齿和齿形链的齿尖要 修缘成三角形而且齿要加工负变位齿, 齿距可以调整或大或小使活动齿和齿形 链有足够的间隙, 如果用滚子链也要转速高时用间歇滚子链 45低速时可以用满 滚子链 49滚子链的滚筒直径要比标准小, 齿也要加工负变位齿使齿和滚子链有 较大的间隙, 滚子链啮合的活动齿可以用一个齿 50或一个以上串联齿 57或并 联齿 58等。 如果传矩大时可以用多排链。 上述齿形链或滚子链与增缩齿轮啮合 转动高转速下变速时轮齿的增大速度快齿形链的移动速度快时有可能互相卡 住,为了防止此现象齿轮固定架 97上安装齿轮 99和 101,它的作用是托起齿形 链或滚子链要和增缩齿轮的啮合角度大使不卡住, 它的另外作用是通过弹簧 98 和 100使齿形链或滚子链的张紧作用, 增缩齿轮转速和变速速度不高时齿轮 99 和 100不用, 可以用间歇齿链或间歇滚子链直接安装增缩齿轮上。
上述增缩齿轮和齿形链啮合技术可以制造平行轴式齿啮合无级变速器和输入 输出轴线同一线的同一轴线式齿啮合转动无级变速器。 先说明平行轴式其变速 器输入轴 1和输出轴 15是平行的, 原动机的旋转经离合器 3转动主动增缩齿轮 4, 其齿轮和齿形链 6啮合转动从动增缩齿轮 5这两个增缩齿轮各一增一缩完成 变速, 变速器正、 反转换档轮系是轴 14另连接的太阳齿轮 7和行星齿轮 8、 齿 圈 9、 行星齿轮架 10、 倒档制动器 11、 前进挡离合器 12、 联合组成正、 反转换 档轮系, 正反转换档技术是公知技术不多提了。 上述正、 反转换档轮系安装在 输出轴上, 如果输入轴上安装时增缩齿轮频繁的正反转使齿形链和滚子链有速 度的突变引起一系列的不良效果, 因此正反转换档齿轮系安装在输出轴上。 输入轴线和输出轴线同一轴线式齿啮合传动无级变速器是输入轴 59上安装输 入小齿轮 61, 其齿轮啮合输入大齿轮 63其齿轮是主动增缩齿轮轴 13上用键固 定安装, 轴 13上固定安装的主动增缩齿轮 4的转动使齿形链 6带动从动增缩齿 轮 5旋转其两个增缩齿轮组成速比变换器, 从动增缩齿轮是轴 14上用键或螺丝 20来固定安装, 轴 14末端用键固定安装输出大齿轮 74两侧分别安装常啮合旋 转的正转输出小齿轮 75和反转输出小齿轮 86。同轴式正、反转换档轮系是正转 输出小齿轮 75是输出轴 96的一侧上安装的空心轴 76两侧外径滚珠 78上接触 旋转, 滚珠 78是空心轴外径上装满的, 滚珠一侧是外径滚珠挡圈 79, 另一侧是 固定安装在正转输出小齿轮 75上的制动鼓 80来定位齿轮在空心轴上的位置, 空心轴内径两侧上安放的滚珠 77是输出轴 96接触, 滚珠 77是空心轴内径上装 满的, 其滚珠一侧是输出轴轴肩, 另一侧是轴套 102来定位空心轴在输出轴上 的位置, 轴套 102是螺丝 103来固定安装在轴上。 制动鼓 80外径上有输出轴上 固定安装的制动带 81其带是液压缸 82和活塞杠杆来松紧, 而且控制齿轮制动, 紧时输出轴 96正传, 松时空档。 液压缸 82的高压油是直通式旋转阀 83进入, 另反转输出小齿轮 86是输出轴 96的另一侧安装的空心轴 87两侧上的外径滚珠 89接触旋转,滚珠 89是空心轴外径上装满的,滚珠 89—侧是固定在齿轮 86上 安装的制动鼓 92,另一侧是外径滚珠挡圈 90来定位齿轮 86在空心轴上的位置, 空心轴内径两侧上滚珠 88是和输出轴 96接触, 滚珠 88是在空心轴内径上装 满的, 一侧是输出轴轴肩, 另一侧是轴套 104来定位空心轴在输出轴 96上的 位置, 轴套 104是螺丝 105来轴上固定安装。 制动带 93是安装在制动鼓 92 的外径上, 带是输出轴 96上固定安装, 带 93是用液压缸 94和活塞杠杆来松 紧而且控制齿轮 86制动, 紧时输出轴 96反转, 松时空档。 高压油是直角式旋 转阀 85进液压缸 94.上述正反转用制动器都紧时输出大齿轮 74制动, 都松时 输出轴 96空档,其带式制动器也可以用多摩檫片式制动器或可控单向超越离合 器来替代, 此时超越离合器拔爪的拔动是液压缸和活塞杠杆来拔动。 正反转齿 轮是悬浮于同一轴上各反方向旋转, 互相不影响而且轴上相对速度不髙。 如果 没有空心轴只安装滚珠或轴承时其互相转动相对转速高两倍, 此时对零件的磨 损大、 噪声也大。
上述同轴式正、 反转换档轮系, 比行星齿轮正反转换档轮系体积小、 用齿轮 个数少、 简单的优点。
上述本发明是解决了摩擦式无级变速器的诸多的缺点而且实现了真正的齿与 齿啮合传动的无级变速器, 使转动扭矩大、 体积小、 结构简单, 可以用在小型、 大型机动车或固定场所上的大、 小机械上。

Claims

权 利 要 求 书
1、 一种齿啮合传动无级变速器, 其特征是- 主要由输入轴 (59)、 主动增缩齿轮轴(13)、 从动增缩齿轮轴 (14)、 输出 轴 (96) 组成, 输入轴线和输出轴线是同一轴线, 主动增缩齿轮轴上安装主动 增缩齿轮 (4), 从动增缩齿轮轴上安装从动增缩齿轮(5), 主动增缩齿轮、 从 动增缩齿轮和齿形链或滚子链啮合组成速比变换器, 速比变换器是单个使用或 一对以上并联或串联使用, 增縮齿轮是由增缩齿轮轴上固定安装的两侧直线槽 盘(16), 此两侧直线槽盘上的直线槽(18) 内安放活动齿的齿臂和直线槽盘外 面两侧在增缩齿轮轴上安装的一起旋转的两侧弧线槽盘 (21 ), 此弧线槽盘上的 弧线槽 (22) 内安放活动齿的齿腕组成, 弧线槽盘是利用电机转动或利用液压 缸内活塞上联接的杠杆推动角度旋转的结构。
2、 权利要求 1所述的齿啮合传动无级变速器, 其特征是:
直线槽盘(16)内面有轮毂(17)利用螺丝或键固定安装在增缩齿轮轴(13) 上, 直线槽(18)是增缩齿轮轴上两个对应安装的直线槽盘(16)上各有 4个 以上均等分布的, 直线槽盘外侧面上有圆形突起部, 弧线槽盘(21 ) 上的弧线 槽(22) 数和分布角度是和直线槽盘上的直线槽数和角度一样, 弧线槽盘上固 定安装行星齿轮盖(27), 此行星齿轮盖内安放滚珠, 此滚珠是接触增缩齿轮轴 上, 弧线槽盘内侧面上有圆形突起部套上直线槽盘外侧面上的圆形突起部, 弧 线槽盘外侧面上固定安装弧形锥齿条(26) 或安装液压缸, 液压缸内有活塞, 活塞连接杠杆, 两个对应的弧线槽盘外侧面上各个固定安装齿圈 (25), 齿圈和 行星齿轮(24) 啮合, 行星齿轮(24)是固定安装在行星齿轮轴 (23) 的两端, 行星齿轮轴安放在直线槽盘轮毂上的轴孔(19) 内, 两个以上的行星齿轮是在 两侧齿圈内均等分布啮合的结构。
3、 权利要求 1所述的齿啮合传动无级变速器, 其特征在于:
活动齿(30) 是由齿身 (32)上连接的齿 (31)和齿身两端面上连接的齿 臂(33), 两侧齿臂外侧面各个连接的齿腕(34), 齿腕上套上的滚筒(35), 和 齿身两端上面和齿的两端面上各连接的挡片 (36) 组成, 活动齿的齿腕安放于 两侧弧线槽内, 两侧弧线槽盘同时角度旋转使活动齿在直线槽内移动, 齿形链 啮合传动的活动齿 (30) 的齿身上的齿 (31 )数是 1个以上的齿或各个不同的 个数齿的活动齿混合使用, 齿(31)是斜齿或人字齿, 使用滚子链啮合传动的 链轮活动齿(50)上的齿数是 1个以上齿串联或并联的结构。
4、 权利要求 1所述的齿啮合传动无级变速器, 其特征在于:
齿形链和活动齿的模数是一样, 齿形链的齿是斜齿或人字齿, 齿距的大小 调整到或大或小, 使用齿形链传动低速时用满齿形链, 髙速时用间歇齿形链, 使用滚子链传动时低速时用满滚子链, 髙速时用间歇滚子链, 传动扭矩大时用 多排链, 张紧用齿轮(99、 101)是安装在固定架 (97)上, 张紧用齿轮(99、 101 )啮合齿形链或滚子链传动, 传动速度低时不用张紧齿轮(99、 101), 用间 歇齿形链或间歇滚子链直接安装在主动、 从动增缩齿轮上的结构。
5、 权利要求 1所述的齿啮合传动无级变速器, 其特征在于:
转动弧线槽盘的动力是用电机(68)转动电机齿轮(69)、 中间齿轮(70)、 蜗杆齿轮(71)和蜗轮, 蜗轮轴转动锥齿轮(72), 锥齿轮啮合转动弧线槽盘上 固定安装的锥齿条 (26)角度旋转, 或油压来转动弧线槽盘, 高压油经过直通 式旋转阀 (66)进液压缸(65)后推动活塞杠杆, 杠杆推动弧线槽盘角度旋转。
6、 权利要求 1所述的齿啮合传动无级变速器, 其特征在于:
输入轴线和输出轴线是同一轴线的, 齿啮合传动无极变速器是输入轴(59) 上固定安装输入小齿轮(61 ), 小齿轮啮合主动增缩齿轮轴 (13)末端上利用键 安装的输入大齿轮, 主动增缩齿轮轴上安装主动增缩齿轮(4)和直通式旋转 阀 (66), 弧线槽盘上安装液压缸 (65), 液压缸内安装活塞, 活塞连接杠杆, 主动增缩齿轮通过齿形链或滚子链啮合从动增缩齿轮(5)从动增缩齿轮轴(14) 上利用键或螺丝 (20) 固定安装从动增缩齿轮 (5), 从动增缩齿轮轴上另安装 直通式旋转阀, 弧线槽盘上安装液压缸, 液压缸内安装活塞, 活塞上连接杠杆, 从动增缩齿轮轴末端利用键固定安装输出大齿轮(74), 输出大齿轮啮合输出轴 (96)上的小齿轮, 输出轴上安装正反转换档齿轮系的结构。
7、 一种齿啮合传动无级变速器, 其特征在于- 平行轴式齿啮合传动无级变速器是主要由输入轴 (2)、 主动增缩齿轮轴、 从动增缩齿轮轴、 输出轴 (15)组成, 输入轴 (2)和输出轴 (15) 是平行的, 平行轴式齿啮合传动无极变速器是由输入轴 (2)通过离合器 (3)接合主动增 缩齿轮轴(13),主动增缩齿轮轴上安装主动增缩齿轮(4),从动增缩齿轮轴(14) 上固定安装从动增缩齿轮(5), 主动、 从动增缩齿轮使用齿形链或滚子链啮合 组成速比变换器, 输出轴上连接正反转换档齿轮系的结构。
PCT/CN2010/001217 2010-08-10 2010-08-10 齿啮合传动无级变速器 WO2012019318A1 (zh)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/CN2010/001217 WO2012019318A1 (zh) 2010-08-10 2010-08-10 齿啮合传动无级变速器

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/CN2010/001217 WO2012019318A1 (zh) 2010-08-10 2010-08-10 齿啮合传动无级变速器

Publications (1)

Publication Number Publication Date
WO2012019318A1 true WO2012019318A1 (zh) 2012-02-16

Family

ID=45567255

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2010/001217 WO2012019318A1 (zh) 2010-08-10 2010-08-10 齿啮合传动无级变速器

Country Status (1)

Country Link
WO (1) WO2012019318A1 (zh)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105697698A (zh) * 2016-03-01 2016-06-22 李方波 一种高效率大扭矩动力传输装置
CN107654597A (zh) * 2017-09-25 2018-02-02 战星罡 一种可变速的消除波动链轮装置

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2078393U (zh) * 1990-05-03 1991-06-05 刘光全 齿轮无级变速器
CN1074987A (zh) * 1992-01-31 1993-08-04 陈友根 齿轮无级变速器
CN2156341Y (zh) * 1993-03-14 1994-02-16 袁永明 机械式无级调速装置
JPH08135742A (ja) * 1994-11-02 1996-05-31 Shizuo Mishima 歯車による回転運動伝達機構及び該機構を用いた無段変速機
CN2273359Y (zh) * 1996-09-09 1998-01-28 秦汝魁 蜂房式齿轮无级变速机构
JP2001153190A (ja) * 1999-11-29 2001-06-08 Oriental Kanzai Kk 無段変速歯車
JP2002327809A (ja) * 2001-04-27 2002-11-15 Katsunori Onishi 差動歯車型無断変速機
US20040014548A1 (en) * 1999-12-17 2004-01-22 Borbolla Gonzalez Teodoro R. Self-contained continuously-variable transmission with mechanical integral torque converter having automatic drive control
CN1529071A (zh) * 2003-10-18 2004-09-15 彭盛章 机械无级变速器
CN1920332A (zh) * 2006-08-11 2007-02-28 汉邦科技股份有限公司 齿轮式双匀速摆线无级变速器
CN101435493A (zh) * 2008-10-23 2009-05-20 金哲跟 齿啮合传动无级变速器

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2078393U (zh) * 1990-05-03 1991-06-05 刘光全 齿轮无级变速器
CN1074987A (zh) * 1992-01-31 1993-08-04 陈友根 齿轮无级变速器
CN2156341Y (zh) * 1993-03-14 1994-02-16 袁永明 机械式无级调速装置
JPH08135742A (ja) * 1994-11-02 1996-05-31 Shizuo Mishima 歯車による回転運動伝達機構及び該機構を用いた無段変速機
CN2273359Y (zh) * 1996-09-09 1998-01-28 秦汝魁 蜂房式齿轮无级变速机构
JP2001153190A (ja) * 1999-11-29 2001-06-08 Oriental Kanzai Kk 無段変速歯車
US20040014548A1 (en) * 1999-12-17 2004-01-22 Borbolla Gonzalez Teodoro R. Self-contained continuously-variable transmission with mechanical integral torque converter having automatic drive control
JP2002327809A (ja) * 2001-04-27 2002-11-15 Katsunori Onishi 差動歯車型無断変速機
CN1529071A (zh) * 2003-10-18 2004-09-15 彭盛章 机械无级变速器
CN1920332A (zh) * 2006-08-11 2007-02-28 汉邦科技股份有限公司 齿轮式双匀速摆线无级变速器
CN101435493A (zh) * 2008-10-23 2009-05-20 金哲跟 齿啮合传动无级变速器

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105697698A (zh) * 2016-03-01 2016-06-22 李方波 一种高效率大扭矩动力传输装置
CN107654597A (zh) * 2017-09-25 2018-02-02 战星罡 一种可变速的消除波动链轮装置

Similar Documents

Publication Publication Date Title
CN101435493B (zh) 齿啮合传动无级变速器
EP2097659A2 (en) Continuously variable transmission-based planetary gear
KR101190375B1 (ko) 무단 변속기
JP2010106957A (ja) ベルト式無段変速機
US9746040B2 (en) Mechanically-actuated direction-sensing roller clutch
EP3012486B1 (en) Flexibly engaged continuously variable transmission gearbox
WO2010031322A1 (zh) 一种适用于电动车的自动变速器
KR20120047454A (ko) 무단 변속기
CN109681593B (zh) 一种双内啮合正倒机构
CN110985636A (zh) 变径链条环轮以及变径链条环轮变速器
JP2010127382A (ja) ベルト式無段変速機
WO2012019318A1 (zh) 齿啮合传动无级变速器
US20050176548A1 (en) Power split transaxle for producing stepless reverse, forward and geared neural speed ratios
JP2006527828A (ja) 機械式トルクコンバータのための螺旋状ギヤラック
WO2007079694A1 (fr) Dispositif de changement de vitesse a variation continue progressive du type a engrenage
CN211852729U (zh) 变径链条环轮以及变径链条环轮变速器
CN210890043U (zh) 方便调节电动车变速装置
CN115095640A (zh) 一种差速器总成及具有该差速器总成的车辆
WO2017206951A1 (zh) 无极变速装置
CN108533700B (zh) 一种无级变速器
KR20090103143A (ko) 유성치차를 이용한 연속 고변속장치
JP5471203B2 (ja) ハイブリッド駆動機構、車両及びその制御方法
KR101026005B1 (ko) 자전거용 무단변속장치
JP7477631B2 (ja) アクチュエータ
CN211501530U (zh) 一种齿传动无级变速器

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: 10855739

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: 10855739

Country of ref document: EP

Kind code of ref document: A1