WO2018153117A1 - 离合器控制机构及其应用的内变速器 - Google Patents

离合器控制机构及其应用的内变速器 Download PDF

Info

Publication number
WO2018153117A1
WO2018153117A1 PCT/CN2017/106984 CN2017106984W WO2018153117A1 WO 2018153117 A1 WO2018153117 A1 WO 2018153117A1 CN 2017106984 W CN2017106984 W CN 2017106984W WO 2018153117 A1 WO2018153117 A1 WO 2018153117A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
control
shaft
pawl
seat
Prior art date
Application number
PCT/CN2017/106984
Other languages
English (en)
French (fr)
Inventor
李激初
Original Assignee
李激初
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 李激初 filed Critical 李激初
Publication of WO2018153117A1 publication Critical patent/WO2018153117A1/zh

Links

Images

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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/12—Freewheels or freewheel clutches with hinged pawl co-operating with teeth, cogs, or the like
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M11/00—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels
    • B62M11/04—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio
    • B62M11/14—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/12—Freewheels or freewheel clutches with hinged pawl co-operating with teeth, cogs, or the like
    • F16D41/125—Freewheels or freewheel clutches with hinged pawl co-operating with teeth, cogs, or the like the pawl movement having an axial component
    • 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
    • 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
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly

Definitions

  • the invention belongs to a transmission, and in particular to a clutch control mechanism and an internal transmission thereof.
  • the internal transmission controls the clutch transmission between the inside of the transmission system and the hub through the clutch to realize the speed ratio control of different gears. Since the internal transmission is completely enclosed inside the hub, the required assembly structure is more complicated, resulting in difficulty in processing parts and high production cost. And the shift control end is located at the outer end of the transmission and is easily damaged by external force.
  • the technical problem solved by the present invention is to provide a novel clutch control mechanism and an internal transmission thereof for the defects of complicated processing and high production cost existing in the existing internal transmission clutch control structure.
  • the clutch is rotated and slidably disposed on the shaft, and the clutch is provided with two sets of clutch structures, wherein one set of clutch structures is drivingly connected with one transmission component, and the other set of clutch structures is coupled with another transmission component.
  • the control mechanism includes a control sleeve, a control rod and a control seat, the control sleeve and the control seat are respectively fitted on the shaft, the control sleeve is axially positioned and connected with the clutch, and the sleeve and the clutch are controlled Freely rotating assembly, the control seat is rotatably assembled on the shaft and connected to a control execution assembly that realizes circumferential rotation along the shaft, the control rod is slidably disposed along the axis of the shaft, and the shaft between one end and the control sleeve To the positioning connection, the other end is in contact with the control cam surface provided on the rotating circumference of the control seat.
  • control sleeve is embedded in the inner hole of the clutch, and the outer wall of the control sleeve is provided with a flange, one side of the flange abuts the axial positioning step of the inner wall of the clutch, and the other side and the shaft An axial positioning connection is achieved between the positioning steps by means of axial positioning members.
  • control sleeve is provided with a positioning hole
  • control rod is provided with a positioning protrusion embedded in the positioning hole
  • the positioning hole and the positioning protrusion are assembled and assembled to realize the control rod and the control sleeve.
  • control sleeve connecting the control rod is connected to the shoulder on the shaft by a compressed spring.
  • the shaft is provided with an axial sliding groove, and the control rod is slidingly embedded in the sliding groove.
  • the internal transmission includes a planetary gear train housed inside the hub, and a clutch disposed between the power input base and the planet carrier of the planetary gear train, the clutch applying the above-described clutch control mechanism of the present invention
  • the inner ring gear of the planetary gear train is engaged by the first pawl and the inner wall of the hub, and the inner ring gear is further engaged with the power input seat by the second pawl, the planet carrier passes the third pawl and The inner wall of the hub is matched;
  • the first pawl, the second pawl, and the third pawl are held in a pop-up state by a compression spring, and the clutch is provided with a slope structure that controls depression of the first pawl.
  • center wheel of the planetary gear train is integrated with the shaft.
  • a one end of the clutch and the power input base form a normally combined transmission state through a sliding jaw structure, and the other end of the clutch forms a clutch fit with the carrier through a jaw clutch structure;
  • the slope structure is The clutch and the carrier are in contact with the first pawl during the separation process, and the first pawl is controlled to cooperate with the inner wall of the hub.
  • an intermediate position of the first pawl is disposed on the inner ring gear through a pin shaft, and an outer end of the first pawl is spring-fitted by a compression spring to engage with a ratchet groove of the inner wall of the hub, and the other end is passed through the inner tooth.
  • the ring is in contact with the ramp structure of the clutch.
  • control execution assembly of the clutch control mechanism includes a cable holder disposed at an outer end of the hub, the cable holder is rotatably fitted at the end of the shaft, and is coaxially rotated and assembled with the control seat, the control seat Mounted on the shaft by mounting the sleeve.
  • control execution assembly further includes a drawstring guide plate fixedly mounted on the shaft by a guide plate mount, the guide plate mount being axially fixed on the shaft by a fixing nut,
  • the guide plate mounting seat is located in the inner ring of the cable holder, the cable guide plate is fixed circumferentially with the guide plate mounting seat, and is axially fixed by the axial snap ring, and the cable seat is rotatably mounted on the guide plate.
  • the drawstring connecting the gear control power assembly is connected to the drawstring seat through the drawstring guide plate.
  • the invention adopts a shaft-mounted control seat, a control rod and a control sleeve to control the clutch, and does not need to process other structures on the shaft, thereby reducing the processing difficulty of the shaft parts, and at the same time between the control seat and the control rod, the control rod and the control
  • the assembly between the sleeves is more convenient, reducing the cost of the internal transmission using the clutch control mechanism.
  • the clutch simultaneously controls the clutch control between the carrier and the ring gear and between the ring gear and the hub.
  • the simplification of the internal structure of the transmission further improves the lightness of the internal transmission and is beneficial to the promotion and application of the internal transmission.
  • Fig. 1 is a schematic view showing the assembly of a clutch control mechanism in the embodiment.
  • Fig. 3 is a schematic view showing the on-axis assembly of the clutch control mechanism and the clutch in the embodiment.
  • Fig. 4 is a schematic view showing the structure of the shaft in the embodiment.
  • Fig. 5 is a schematic view showing the assembly of the internal transmission applied in the embodiment.
  • Fig. 6 is a schematic view showing the first gear state of the internal transmission in the embodiment.
  • Figure 7 is a schematic view of the first pawl state of the internal transmission in the first gear in the embodiment.
  • Fig. 8 is a schematic view showing the second gear state of the internal transmission in the embodiment.
  • Figure 9 is a schematic view of the first pawl state of the internal transmission in the second gear in the embodiment.
  • Figure 10 is a schematic view showing the state of the third gear position of the internal transmission in the embodiment.
  • Figure 11 is an exploded perspective view of the control execution assembly of the internal transmission in the embodiment.
  • 6-Control Execution Components 61-drawing seat, 62-drawing guide, 63-guide mounting, 64-control torsion spring, 65-mounting sleeve, 66-axial snap ring, 67-retaining nut.
  • the clutch 1 in this embodiment is a jaw clutch mounted on a shaft, and the clutch 1 is rotatably mounted on the shaft 3 , and a control sleeve 11 is mounted on the inner ring of the clutch 1 .
  • Control The rod 12, the control seat 13, the spring 14 and the axial positioning member 15 are used to control the linear movement of the clutch 1 along the axis of the shaft 3 to realize the clutching action without affecting the clutch directly transmitting the rotational power to the two transmission members. .
  • control sleeve 11 is coaxially fitted with the clutch 1 on the shaft 3, and the control sleeve 11 is axially slidable relative to the shaft 3 and the clutch 1.
  • the control sleeve 11 is a sleeve having a stepped structure flange 111.
  • the member, the control sleeve 11 is assembled between the inner ring of the clutch 1 and the shaft 3, and a stepped end surface of the flange 111 is in contact with the axial positioning step 104 of the inner ring of the clutch 1 to realize a connection between the clutch 1 and the control sleeve 11.
  • a groove for assembling the axial positioning member 15 is also provided on the inner ring of the clutch 1, and the axial positioning member 15 can be an axial positioning snap ring by assembling the axial positioning member 15 and the flange 111.
  • the other end face contact realizes the positioning of the other axial direction between the clutch 1 and the control sleeve 11, and finally realizes the direct reliable axial positioning of the clutch 1 and the control sleeve 11, that is, the control sleeve 11 can control the clutch 1 along The axial direction of the shaft 3 slides to the left and right.
  • a clearance fit is used between the outer ring of the control sleeve 11 and the inner ring of the clutch 1, and between the flange 111 and the axial positioning step 104 of the clutch 1 and the axial positioning member 15, to realize the clutch 1 and the control sleeve.
  • the free-rotation assembly between 11 means that the control sleeve 11 does not affect the rotational transmission of the clutch 1 itself.
  • the control seat 13 is a rotary member that is rotatably mounted on the shaft 3.
  • a control cam surface 131 having a height difference is provided on the rotation circumference of the control seat 13, and the control cam surface 131 is disposed at a rotary end surface opposite to the control sleeve 11.
  • the vertical distance between the point on the control cam surface 131 to the control sleeve 11 is changed by controlling the height difference on the cam surface 131, and the control seat 13 is pushed and controlled by the control rod 12 which is axially slidably positioned on the shaft 3.
  • the sleeve 11 slides axially, which in turn drives the clutch 1 to move axially.
  • the control rod 12 is a rod-shaped member, and the two ends are connected to the control sleeve 11 and the control seat 13, respectively.
  • the end of the control rod 12 near the control seat 13 is a pushing end portion 121 of the round head.
  • the pushing end portion 121 is in contact with the control cam surface 131 of the control seat 13 and forms a cam pair fit with the control seat 13.
  • a positioning protrusion 122 is disposed on the inner end of the control sleeve 11 corresponding to the control rod 11 .
  • a positioning hole 112 is disposed in the inner ring of the control sleeve 11 , and the positioning protrusion 122 is engaged with the positioning hole 112 to control the lever 12 and
  • An axial positioning connection is realized between the positioning sleeves 11, and the control cam surface 131 is controlled by the rotation of the control seat 13
  • the rod 12 is axially moved to drive the control sleeve 11 to linearly slide in the axial direction.
  • the shaft 3 is provided with a rotary mounting section 303 for rotating the assembly control sleeve 11, the diameter of the rotary mounting section 303 being larger than the outer diameter of the shaft section of the one end mounting control seat 13, on the rotating mounting section 303
  • An axial sliding slot 302 is defined in the axial direction, and the control rod 12 is slidably embedded in the axial sliding slot 302, so that the control rod 12 is slidably restricted along the axial direction of the shaft 3, and the control rod 12 is partially embedded in the shaft 3.
  • the installation prevents the control rod 12 from occupying too much space in the inner ring of the control sleeve 11, and can effectively reduce the radial size of the inner ring.
  • the control sleeve 11, the control rod 12 and the control seat 13 cooperate to drive the clutch from right to left in Fig. 3, and the compressed spring 14 is used to push the clutch axially back from left to right.
  • a shaft shoulder 301 is disposed on the shaft 3 of the control sleeve 11 away from the end of the control seat 13, and a compression spring 14 is disposed between the shoulder 301 and the control sleeve 11, and the compressed spring 14 functions as a control seat 13 After the control sleeve 11 is pushed to the left, the control sleeve 11 is driven back to the right.
  • the illustrated internal transmission is a preferred embodiment of the clutch and clutch control mechanism of the present embodiment, including a planetary gear train, a clutch 1, a shaft 3, a hub 4, and a power input base 5.
  • the shaft 3 is a wheel axle
  • the planetary gear train is enclosed between the shaft 3 and the hub 4, and the power input base 5 is connected to the power input end of the planetary gear train through the clutch 1 through the clutch 1, and the power input seat 5 is controlled.
  • the control execution component 6 is used to control the control seat in the clutch control mechanism.
  • the planetary gear train in this embodiment includes an inner ring gear 21, a first pawl 211, a second pawl 212, a carrier 22, a center wheel 23, and a plurality of planet wheels.
  • the inner ring of the inner ring gear 21 is assembled by a single transmission between the second pawl 212 and the power input base 5, and the power input base 5 is connected with a power input transmission member externally connected to the internal transmission, such as a flywheel, and the inner ring gear 21 passes through
  • a pawl 211 is unidirectionally coupled with the inner wall of the hub 4, and the outer ring of the carrier 22 is unidirectionally coupled with the inner portion of the hub 4 by the third pawl 213.
  • the one-way transmission coordination referred to in this embodiment is The driving direction in which the wheels connected to the hub 4 are rotated forward.
  • the first pawl 211, the second pawl 212, and the third pawl 213 are all assembled by a compression spring, and maintain the initial state in a pop-up state (ie, a state of one-way transmission), specifically how to pass the pressure
  • the spring assembly pawl is a common technical means in the internal transmission, and the embodiment will not be described herein.
  • the power input end of the planetary gear train may be the inner ring gear 21 or the carrier 22 depending on the gear position.
  • the clutch 1 in this embodiment is disposed between the power input base 5 and the carrier 22, see FIG. 2 again.
  • the clutch 1 of the present embodiment is respectively provided with a first clutch structure 101 and a second clutch structure 102 at both ends, wherein the first clutch structure 101 is a plurality of protrusions disposed on the circumference of the clutch end face, and the inner ring end surface of the carrier 22 The plurality of grooves are arranged to be engaged with each other, and the jaw clutch structure can be separated and combined.
  • the second clutch structure 102 is a plurality of protrusions disposed on the outer circumference of the other end surface of the clutch, and is disposed with the inner ring of the power input base 5
  • the axial groove is slidably fitted to form a sliding jaw structure in a normally combined state.
  • the second clutch structure 102 is always in a power transmission state with the power input base 5. .
  • the clutch 1 of the present embodiment is engaged with the carrier by the inner ring gear 21, and the outer ring of the clutch 1 is further provided with a circumferentially disposed ramp structure 103.
  • the outer diameter of the clutch on one side of the ramp structure 103 is larger than the other side.
  • the outer diameters are connected to each other by a ramp structure 103, and a low plane 1031 (larger clutch outer diameter) and a high plane 1032 (small clutch outer diameter) are formed on both sides of the ramp structure 103, and the ramp structure 103
  • the first pawl 211 can be controlled to change from the pop-up state to the depressed state.
  • the intermediate position of the first pawl 211 is disposed on the inner ring gear 21 by the pin rotation, and the outer ratchet end of the first pawl 211 is springed up by the compression spring to the ratchet groove of the inner wall of the hub.
  • the inner side is in contact with the outer diameter of the clutch through the ring gear 21, and the outer side of the first pawl 211 is leveraged by the transition between the upper and lower faces of the ramp structure 103. Pressing, the inner ring gear 21 and the hub 4 are separated.
  • This embodiment is a three-speed internal transmission, and it is not necessary to control the center wheel 23, and the center wheel 23 is fixedly assembled with the shaft 3. In order to save assembly costs, the center wheel 23 can be integrally formed on the shaft 3.
  • the inner ring gear 21 transmits the rotational power to the planetary gear train for deceleration transmission, and then is output by the carrier 22 through the third pawl.
  • the wheel that drives the hub is rotated, the gear is at a low speed, and the power transmission path is as indicated by an arrow in FIG. 6, and the state of the first pawl 211 is as shown in FIG.
  • the power is entered by the power input base 5 and directly transmitted through the first pawl 211.
  • the gear is the direct gear
  • the rotation speed of the hub 4 exceeds the rotation speed of the carrier 22, and the third pawl 213 is overtaken, and the power transmission path is as indicated by the arrow in FIG.
  • the state of the first pawl 211 is as shown in FIG.
  • the high position of the control cam surface of the block control seat 13 is in contact with the control rod, and the control seat 13 continues to push the control sleeve 11 to the left side of the planet carrier through the control rod 12 to change the clutch 1 and the carrier 22 into a coupled state.
  • the inner side of the first pawl 211 is kept in contact with the lower surface of the outer ring of the clutch 1, and the inner ring gear 21 and the hub 4 are in a one-way power transmission state.
  • the power is entered by the power input base 5, and the clutch 1 is passed.
  • the gear carrier 22 transmits the rotational power to the planetary gear train for the speed increase transmission, and then the inner ring gear 22 is outputted from the first pawl 211 to the hub 4, and the wheel connected to the hub is rotated.
  • the speed increase gear, the rotation speed of the hub 4 and the inner ring gear 21 exceeds the rotation speed of the power input base 5, the second pawl 212 is overtaken, and the power transmission path is as indicated by an arrow in FIG. 10, and the state of the first pawl 211 remains as Figure 9 shows.
  • the control execution assembly 6 of the clutch control mechanism includes a cable holder 61, a cable guide 62, a guide plate mount 63, a control torsion spring 64, a mounting sleeve 65, and an axial direction. Retaining ring 66 and fixing nut 67.
  • the cord holder 61 and the control seat 13 are rotatably mounted on the end of the shaft 3 through the mounting sleeve 65, and are rotatably assembled with the hub by the bead frame assembly 41, between the cord holder 61 and the mounting sleeve 65, and mounted.
  • the sleeve 65 and the control seat 13 are respectively connected by a circumferential positioning structure, and the cable seat 61 is connected with a cable system outside the internal transmission, and the cable seat 61 is driven to rotate circumferentially relative to the shaft 3 by the cable, thereby driving the clutch.
  • the control seat 13 of the control mechanism rotates, and at the same time, the rope base 61 and the shaft 3 are connected by the control torsion spring 64 to realize the elastic return of the rope holder 61.
  • the cable guiding plate 62 is circumferentially assembled on the outer side of the cable seat 61 by the guiding plate mounting seat 63 for axial positioning of the cable seat, and is also used for guiding the pulling rope into the cable seat, and the guiding plate is installed.
  • the seat 63 is assembled by circumferentially positioning with the shaft 3 through a non-circular flat position, and the positioning and assembly are realized by the circumferentially fitting projections and grooves between the pull cord guide plate 62 and the guide plate mounting seat 63, and at the same time, guided
  • An axial snap ring 66 is disposed on the outer side of the plate mounting seat 63 as an axial positioning assembly of the cable guide plate 62.
  • the shaft 3 on the outer side of the guide plate mounting seat 63 is screwed to the fixing nut 67 to realize the entire clutch control mechanism and the control execution component.
  • the shaft 3 is axially locked.
  • the guide plate mounting seat 63 is embedded in the inner ring of the cable holder 61.
  • the flywheel When the flywheel is replaced: the axial cable collar 66 is removed to take out the cable guide plate 62 and the cable holder 61, so that the nut is not removed.
  • the flywheel replacement of the power input base of the internal transmission is performed without affecting the internal structural assembly.
  • the internal transmission to which the present invention is applied can be applied to a hub including a bicycle, an electric assist bicycle or a motorcycle, and is not limited to the three-speed internal transmission described in the present embodiment, and those skilled in the art can vary according to the transmission speed ratio.
  • a hub including a bicycle, an electric assist bicycle or a motorcycle
  • the present embodiments are not enumerated herein.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

一种离合器控制机构及其应用的内变速器，通过轴（3）上装配的控制座（13）、控制杆（12）和控制套筒（11）控制离合器（1），不需要在轴（3）上加工其他的结构，降低了轴零件的加工难度，同时控制座（13）和控制杆（12）之间、控制杆（12）和控制套筒（11）之间的装配方式更加方便，降低了使用该离合器控制机构的内变速器成本，在内变速器中，该离合器（1）同时控制行星架（22）和内齿圈（21）之间以及内齿圈（21）和花鼓（4）之间的离合控制，简化了变速器内部构造，进一步提高了内变速器的轻便化，有利于内变速器的推广应用。

Description

离合器控制机构及其应用的内变速器
本申请要求于2017年02月27日提交中国专利局、申请号为201710108815.5、发明名称为“离合器控制机构及其应用的内变速器”的专利申请，其全部内容通过引用结合在本申请中。
技术领域
本发明属于变速器，具体涉及一种离合器控制机构及其应用的内变速器。
背景技术
内变速器通过离合器控制传动系统内部和花鼓之间的离合传动，实现不同挡位的速比控制。由于内变速器全部封装在花鼓内部，其要求的装配结构更复杂，导致零部件的加工难度大，生产成本高。并且变速控制端位于变速器外侧端部，容易被外力破坏。
如申请号为03204051.2的中国专利文件中公开的一种改进的内变速器轮毂轴及其具有其轮毂的内变速器，其中采用的离合器的控制包括套装在轮毂轴上的内、外套件，通过在套件上加工异形的透空路径，通过配合的定位销一同实现离合器的轴向离合运动，套件的加工方式复杂，在装配过程中需要将定位销和套件一同装配好再套装在轮毂轴上，装配困难，定位销的传动方式容易磨损，导致内变速器的使用寿命有限。
随着内变速器在自行车上的应用越来越广泛，如何降低内变速器的生产成本和装配难题显得越发重要。
发明内容
本发明解决的技术问题是：针对现有的内变速器离合器控制结构存在的加工复杂、生产成本高的缺陷，提供一种新型的离合器控制机构及其应用的内变速器。
本发明采用如下技术方案实现：
离合器控制机构，离合器转动和滑动套装在轴上，所述离合器上设有两组离合结构，其中一组离合结构与一传动部件传动连接，另一组离合结构与另一传动部件可离合连接，所述控制机构包括控制套筒、控制杆和控制座，所述控制套筒和控制座分别套装在轴上，所述控制套筒与离合器之间轴向定位连接，并且控制套筒和离合器之间自由旋转装配，所述控制座旋转装配在轴上，并与实现沿轴的周向旋转的控制执行组件连接，所述控制杆沿轴的轴线方向滑动设置，一端与控制套筒之间轴向定位连接，另一端与控制座的转动圆周上设置的控制凸轮面接触。
进一步的，所述控制套筒嵌装在离合器内孔，所述控制套筒的外壁设有凸缘，所述凸缘的一侧与离合器内壁的轴向定位台阶抵接，另一侧和轴向定位台阶之间通过轴向定位件实现轴向定位连接。
进一步的，所述控制套筒上设有定位孔，所述控制杆上设有嵌入定位孔中的定位凸块，所述定位孔和定位凸块之间嵌合装配，实现控制杆和控制套筒之间的轴向定位连接。
进一步的，所述控制套筒连接控制杆的远端通过压缩的弹簧与轴上的轴肩连接。
进一步的，所述轴上设有轴向的滑槽，所述控制杆滑动嵌装在滑槽内。
内变速器，包括封装在花鼓内部的行星轮系、以及设置在动力输入座和行星轮系的行星架之间的离合器，所述离合器应用了本发明上述的离合器控制机构；
另外，所述行星轮系的内齿圈通过第一棘爪和花鼓内壁配合，并且，所述内齿圈还通过第二棘爪与动力输入座配合，所述行星架通过第三棘爪和花鼓内壁配合；
所述第一棘爪、第二棘爪和第三棘爪通过压簧保持弹起状态，所述离合器上设有控制第一棘爪压下的斜坡结构。
进一步的，所述行星轮系的中心轮与轴为一体结构。
进一步的，所述离合器一端与动力输入座之间通过滑动牙嵌式结构形成常结合传动状态，所述离合器另一端与行星架之间通过牙嵌式离合结构形成离合配合；所述斜坡结构在离合器与行星架分离过程中与第一棘爪接触，控制第一棘爪弹起后与花鼓内壁配合。
进一步的，所述第一棘爪的中间位置通过销轴设置在内齿圈上，第一棘爪的外端通过压簧弹起与花鼓内壁的棘槽嵌合，另一端与穿过内齿圈与离合器的斜坡结构接触。
在本发明中，所述离合器控制机构的控制执行组件包括设置在花鼓外端的拉绳座，所述拉绳座转动套装在轴端部，并与控制座同轴旋转传动装配，所述控制座通过安装套筒旋转安装在轴上。
进一步的，所述控制执行组件还包括拉绳导向板，所述拉绳导向板通过导向板安装座固定安装在轴上，所述导向板安装座通过固定螺母轴向固定在轴上，所述导向板安装座位于拉绳座的安装内圈中，所述拉绳导向板与导向板安装座周向固定，并通过轴向卡环轴向固定，所述拉绳座转动安装在导向板安装座上，连接挡位控制动力组件的拉绳通过拉绳导向板与拉绳座连接。
本发明采用轴上装配的控制座、控制杆和控制套筒控制离合器，不需要在轴上加工其他的结构，降低了轴零件的加工难度，同时控制座和控制杆之间、控制杆和控制套筒之间的装配方式更加方便，降低了使用该离合器控制机构的内变速器成本，在内变速器中，该离合器同时控制行星架和内齿圈之间以及内齿圈和花鼓之间的离合控制，简化了变速器内部构造，进一步提高了内变速器的轻便化，有利于内变速器的推广应用。
以下结合附图和具体实施方式对本发明做进一步说明。
附图说明
图1为实施例中的离合器控制机构的装配示意图。
图2为实施例中的离合器控制机构分解示意图。
图3为实施例中的离合器控制机构及离合器的轴上装配示意图。
图4为实施例中的轴结构示意图。
图5为实施例中应用的内变速器装配示意图。
图6为实施例中内变速器的第一挡位状态示意图。
图7为实施例中内变速器在第一挡位时的第一棘爪状态示意图。
图8为实施例中的内变速器的第二挡位状态示意图。
图9为实施例中的内变速器在第二挡位时的第一棘爪状态示意图。
图10为实施例中内变速器的第三档位状态示意图。
图11为实施例中的内变速器的控制执行组件分解示意图。
图中标号：
1-离合器，101-第一离合结构，102-第二离合结构，103-斜坡结构，1031-低位面，1032-高位面，104-轴向定位台阶，11-控制套筒，111-凸缘，112-定位孔，12-控制杆，121-推动端部，122-定位凸块，13-控制座，131-控制凸轮面，14-弹簧，15-轴向定位件，
21-内齿圈，211-第一棘爪，212-第二棘爪，213-第三棘爪，22-行星架，23-中心轮，
3-轴，301-轴肩，302-轴向滑槽，303-旋转安装段，
4-花鼓，401-棘槽，41-珠架组件，
5-动力输入座，
6-控制执行组件，61-拉绳座，62-拉绳导向板，63-导向板安装座，64-控制扭簧，65-安装套筒，66-轴向卡环，67-固定螺母。
具体实施方式
实施例一
参加图1、图2和图3，本实施例中的离合器1为装配在轴上的牙嵌式离合器，离合器1旋转装配在轴3上，在离合器1的内圈装配有控制套筒11、控 制杆12、控制座13、弹簧14和轴向定位件15等部件，用于控制离合器1沿轴3的轴线方向直线动作，实现离合动作，同时不影响离合器在两个传动部件直接传递旋转动力。
具体的，控制套筒11与离合器1同轴套装在轴3，控制套筒11可相对轴3以及离合器1之间轴向滑移，控制套筒11为一具有台阶结构凸缘111的套筒构件，控制套筒11装配在离合器1内圈和轴3之间，通过凸缘111的一个台阶端面与离合器1内圈的轴向定位台阶104接触，实现离合器1和控制套筒11之间一个轴向方向的定位，在离合器1内圈还设置用于装配轴向定位件15的槽，该轴向定位件15可为轴向定位卡环，通过装配轴向定位件15与凸缘111的另一个端面接触，实现离合器1和控制套筒11之间另一个轴向方向的定位，最终一同实现离合器1和控制套筒11直接的可靠轴向定位，即控制套筒11能够控制离合器1沿轴3的轴向左右滑移。同时，控制套筒11的外圈和离合器1的内圈之间、以及凸缘111和离合器1的轴向定位台阶104及轴向定位件15之间采用间隙配合，实现离合器1和控制套筒11之间的自由转动装配，即控制套筒11不会影响离合器1本身的旋转传动。
控制座13为一旋转套装在轴3上的回转构件，在控制座13的转动圆周上设有具备高度差的控制凸轮面131，该控制凸轮面131设置在与控制套筒11相对的回转端面上，控制凸轮面131上的点到控制套筒11之间的垂直距离通过控制凸轮面131上的高度差进行变化，控制座13通过在轴3上轴向滑移定位的控制杆12推动控制套筒11轴向滑移，进而带动离合器1轴向动作。
控制杆12为一杆状构件，两端分别连接控制套筒11和控制座13。具体的，控制杆12靠近控制座13的端部为圆头的推动端部121，该推动端部121与控制座13的控制凸轮面131接触，与控制座13之间形成一个凸轮副配合，控制杆12靠近控制套筒11的端部设置定位凸块122，对应的，在控制套筒11的内圈设有一定位孔112，定位凸块122与定位孔112嵌合，将控制杆12和定位套筒11之间实现轴向定位连接，控制凸轮面131随着控制座13的转动，推动控 制杆12轴向动作，驱动控制套筒11轴向直线滑移。
结合参见图4，轴3上设有用于旋转装配控制套筒11的旋转安装段303，该旋转安装段303的直径要大于一端安装控制座13的轴段外径，在该旋转安装段303上沿轴向开设轴向滑槽302，控制杆12滑动嵌装在该轴向滑槽302内，实现控制杆12沿轴3的轴线方向滑移限位，同时将控制杆12部分嵌入轴3内安装，避免控制杆12过多地占用控制套筒11内圈的空间，可有效降低控制内圈的径向尺寸。
控制套筒11、控制杆12和控制座13配合实现图3中从右向左推动离合器，压缩的弹簧14则用于从左向右推动离合器轴向回位。控制套筒11远离控制座13一端的轴3上设有轴肩301，在该轴肩301和控制套筒11之间设有压缩的弹簧14，该压缩的弹簧14的作用是在控制座13将控制套筒11向左推动后，驱动控制套筒11向右回位。
结合参见图5和图1-4，图示中的内变速器为采用本实施例的离合器及离合器控制机构的优选实施方案，包括行星轮系、离合器1、轴3、花鼓4、动力输入座5以及控制执行组件6，轴3为车轮轴，行星轮系封装在轴3和花鼓4之间，动力输入座5通过离合器1与行星轮系的动力输入端通过离合器1连接，控制动力输入座5和行星轮系的动力输入端之间以及行星轮系的棘爪离合控制，控制执行组件6则用于控制离合器控制机构中的控制座13.
具体的，本实施例中的行星轮系包括内齿圈21、第一棘爪211、第二棘爪212、行星架22、中心轮23和若干行星轮。其中内齿圈21的内圈通过第二棘爪212与动力输入座5之间单传动装配，动力输入座5与内变速器外部连接的动力输入传动件连接，如飞轮，内齿圈21通过第一棘爪211与花鼓4的内壁单向传动配合，行星架22的外圈通过第三棘爪213与花鼓4的内部单向传动配合，本实施例中所指的单向传动配合均是至驱动花鼓4连接的车轮向前转动的传动方向。在这里，第一棘爪211、第二棘爪212和第三棘爪213均通过压簧装配，并保持初始状态为弹起状态(即单向传动的状态)，具体如何通过压 簧装配棘爪为内变速器中常用的技术手段，本实施例在此不做赘述。
行星轮系的动力输入端根据挡位的不同，可以为内齿圈21或是行星架22，本实施例中的离合器1设置在动力输入座5和行星架22之间，再次参见图2，本实施例的离合器1在两端分别设有第一离合结构101和第二离合结构102，其中，第一离合结构101为设置在离合器端面圆周的若干凸起，与行星架22的内圈端面设置的若干凹槽相互嵌合，能过分离和结合的牙嵌式离合结构，第二离合结构102为设置在离合器另一端面外圆周的若干凸起，与动力输入座5内圈设置的若干轴向凹槽滑动嵌合，形成常结合状态的滑动牙嵌式结构，第一离合结构101与行星架22分离或结合的过程中，第二离合结构102始终与动力输入座5保持动力传动状态。
本实施例的离合器1穿过内齿圈21与行星架离合动作，在离合器1的外圈还设有沿周向设置的斜坡结构103，斜坡结构103的一侧的离合器外径大于另一侧的外径，相互之间通过斜坡结构103连接，在斜坡结构103的两侧分别形成低位面1031(较大的离合器外径)和高位面1032(较小的离合器外径)，该斜坡结构103与设置在内齿圈21和花鼓4之间的第一棘爪211接触，可控制第一棘爪211从弹起状态变换为压下状态。
如图7和图9所示，第一棘爪211的中间位置通过销轴转动设置在内齿圈21上，第一棘爪211的外侧棘齿端通过压簧弹起与花鼓内壁的棘槽嵌合，形成单向传动，内侧则穿过内齿圈21与离合器的外径接触，经过斜坡结构103两端的高位面和低位面之间的变换，通过杠杆作用将第一棘爪211的外侧压下，使内齿圈21和花鼓4分离。
本实施例为三速内变速器，不需要控制中心轮23，中心轮23与轴3之间固定装配，为了节省装配成本，可将中心轮23在轴3上一体加工成型。
以下结合图6-图10详细说明本实施例的三速内变速器的挡位传动状态。
当控制座13的控制凸轮面的低位与控制杆接触时，控制套筒11及离合器1在弹簧14的作用下向右推动推动，此时离合器1与行星架22之间为动力分 离状态，并且离合器的斜坡结构103的高位面1032与第一棘爪211的内侧接触，将第一棘爪211控制为压下状态，使内齿圈21与花鼓4之间为动力分离状态，此时动力由动力输入座5进入，通过第二棘爪212传递至内齿圈21，内齿圈21将旋转动力传入行星轮系进行减速传动，然后由行星架22经第三棘爪输出至花鼓4，带动花鼓连接的车轮转动，该挡位为低速档，动力传递路线如图6中的箭头所示，第一棘爪211的状态如图7所示。
当控制座13的控制凸轮面的中间位置与控制杆接触时，控制座13通过控制杆12推动控制套筒11向左侧的行星架靠近，此时离合器1与行星架22之间仍为分离状态，但是在离合器1向左移动的过程中，离合器1的外圈与第一棘爪211内侧接触的位置由高位面1032经斜坡结构103变换至低位面1031，第一棘爪211的内侧失去离合器的限制，在自身压簧的作用下弹起，变换内齿圈21与花鼓4之间为单向动力传动状态，此时，动力由动力输入座5进入，直接通过第一棘爪211传递至花鼓4输出，带动花鼓连接的车轮转动，该挡位为直接挡，花鼓4的转速超过行星架22的转速，第三棘爪213被超越，动力传递路线如图8中的箭头所示，第一棘爪211的状态如图9所示。
挡控制座13的控制凸轮面的高位与控制杆接触，控制座13继续通过控制杆12推动控制套筒11向左侧的行星架靠近，将离合器1与行星架22之间变换为结合状态，此时第一棘爪211的内侧保持与离合器1外圈的低位面接触，内齿圈21与花鼓4之间为单向动力传递状态，此时，动力由动力输入座5进入，通过离合器1传递至行星架22，行星架22将旋转动力传入行星轮系进行增速传动，然后由内齿圈22由第一棘爪211输出至花鼓4，带动花鼓连接的车轮转动，该挡位为增速挡，花鼓4及内齿圈21的转速超过动力输入座5的转速，第二棘爪212被超越，动力传递路线如图10中的箭头所示，第一棘爪211的状态仍然如图9所示。
如图11所示，在内变速器中，离合器控制机构的控制执行组件6包括拉绳座61、拉绳导向板62、导向板安装座63、控制扭簧64、安装套筒65、轴向 卡环66和固定螺母67。其中拉绳座61及控制座13均通过安装套筒65转动安装在轴3的端部，并与花鼓之间通过珠架组件41转动装配，拉绳座61和安装套筒65之间以及安装套筒65和控制座13之间分别通过周向定位结构连接，拉绳座61与内变速器外部的拉绳系统连接，通过拉绳驱动拉绳座61相对于轴3周向转动，进而驱动离合器控制机构的控制座13转动，同时，拉绳座61和轴3之间通过控制扭簧64连接，实现拉绳座61的弹性回位。拉绳导向板62通过导向板安装座63周向定位装配在拉绳座61的外侧，用于拉绳座的轴向定位同时，还用于对拉绳引入拉绳座进行导向，导向板安装座63通过与轴3之间通过非圆扁位周向定位装配，拉绳导向板62和导向板安装座63之间通过周向嵌合的凸起和凹槽实现定位装配，同时，在导向板安装座63的外侧设置轴向卡环66，作为拉绳导向板62的轴向定位装配，导向板安装座63外侧的轴3上螺接固定螺母67，实现整个离合器控制机构及控制执行组件在轴3的轴向锁紧。导向板安装座63嵌装在拉绳座61的内圈中，在更换飞轮时：取掉轴向卡环66即可取出拉绳导向板62和拉绳座61，实现不拆取螺母的情况下进行内变速器的动力输入座连接的飞轮更换，而不会影响内部结构装配。
本发明所应用的内变速器可应用在包括自行车、电动助力自行车或摩托车的轮毂上，并且也不仅限于本实施中所述的三速内变速器，本领域技术人员可根据传动速比的不同，采用以上实施例在本权利要求范围内的各种相似实施方式，本实施例在此不一一列举。

Claims (10)

  1. 一种离合器控制机构，离合器转动和滑动套装在轴上，所述离合器上设有两组离合结构，其中一组离合结构与一传动部件传动连接，另一组离合结构与另一传动部件可离合连接，其特征在于，
    所述控制机构包括控制套筒、控制杆和控制座，所述控制套筒和控制座分别套装在轴上，所述控制套筒与离合器之间轴向定位连接，并且控制套筒和离合器之间自由旋转装配，所述控制座旋转装配在轴上，并与实现沿轴的周向旋转的控制执行组件连接，所述控制杆沿轴的轴线方向滑动设置，一端与控制套筒之间轴向定位连接，另一端与控制座的转动圆周上设置的控制凸轮面接触。
  2. 根据权利要求1所述的离合器控制机构，所述控制套筒嵌装在离合器内孔，所述控制套筒的外壁设有凸缘，所述凸缘的一侧与离合器内壁的轴向定位台阶抵接，另一侧和轴向定位台阶之间通过轴向定位件实现轴向定位连接。
  3. 根据权利要求2所述的离合器控制机构，所述控制套筒上设有定位孔，所述控制杆上设有嵌入定位孔中的定位凸块，所述定位孔和定位凸块之间嵌合装配，实现控制杆和控制套筒之间的轴向定位连接。
  4. 根据权利要求3所述的离合器控制机构，所述控制套筒连接控制杆的远端通过压缩的弹簧与轴上的轴肩连接。
  5. 根据权利要求4所述的离合器控制机构，所述轴上设有轴向的滑槽，所述控制杆滑动嵌装在滑槽内。
  6. 内变速器，包括封装在花鼓内部的行星轮系、以及设置在动力输入座和行星轮系的行星架之间的离合器，其特征在于，所述离合器应用权利要求1-5中所述的离合器控制机构；
    所述行星轮系的中心轮与轴固定连接，所述行星轮系的内齿圈通过第一棘爪和花鼓内壁配合，所述内齿圈还通过第二棘爪与动力输入座配合，所述行星 架通过第三棘爪和花鼓内壁配合；
    所述第一棘爪、第二棘爪和第三棘爪通过压簧保持弹起状态，所述离合器上设有控制第一棘爪压下的斜坡结构。
  7. 根据权利要求6所述的内变速器，所述离合器一端与动力输入座之间通过滑动牙嵌式结构形成常结合传动状态，所述离合器另一端与行星架之间通过牙嵌式离合结构形成离合配合；
    所述斜坡结构在离合器与行星架分离过程中与第一棘爪接触，控制第一棘爪弹起后与花鼓内壁配合。
  8. 根据权利要求7所述的内变速器，所述第一棘爪的中间位置通过销轴设置在内齿圈上，第一棘爪的外端通过压簧弹起与花鼓内壁的棘槽嵌合，另一端与穿过内齿圈与离合器的斜坡结构接触。
  9. 根据权利要求6-8中任一项所述的内变速器，所述离合器控制机构的控制执行组件包括设置在花鼓外端的拉绳座，所述拉绳座转动套装在轴端部，并与控制座同轴旋转传动装配，所述控制座通过安装套筒旋转安装在轴上。
  10. 根据权利要求9所述的内变速器，所述控制执行组件还包括拉绳导向板，所述拉绳导向板通过导向板安装座固定安装在轴上，所述导向板安装座位于拉绳座的安装内圈中，所述导向板安装座通过固定螺母轴向固定在轴上，所述拉绳导向板与导向板安装座周向固定，并通过轴向卡环轴向固定，所述拉绳座转动安装在导向板安装座上，连接挡位控制动力组件的拉绳通过拉绳导向板与拉绳座连接。
PCT/CN2017/106984 2017-02-27 2017-10-20 离合器控制机构及其应用的内变速器 WO2018153117A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201710108815.5A CN108506368B (zh) 2017-02-27 2017-02-27 离合器控制机构及其应用的内变速器
CN201710108815.5 2017-02-27

Publications (1)

Publication Number Publication Date
WO2018153117A1 true WO2018153117A1 (zh) 2018-08-30

Family

ID=63253104

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2017/106984 WO2018153117A1 (zh) 2017-02-27 2017-10-20 离合器控制机构及其应用的内变速器

Country Status (3)

Country Link
CN (1) CN108506368B (zh)
TW (1) TWI658964B (zh)
WO (1) WO2018153117A1 (zh)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN201021345Y (zh) * 2007-01-22 2008-02-13 福隆尖端科技股份有限公司 自行车的内变速器
US20100160109A1 (en) * 2008-12-24 2010-06-24 Sun Race Sturney Archer, Inc. Fixed gear internal gear hub
JP2012066723A (ja) * 2010-09-24 2012-04-05 Ntn Corp 回生機構を備えた電動補助自転車
CN202827982U (zh) * 2012-04-23 2013-03-27 谢定义 一种自行车内变速装置
CN103569306A (zh) * 2013-11-19 2014-02-12 李激初 自行车内变速器
CN204056187U (zh) * 2014-08-15 2014-12-31 李激初 一种自行车内变速器
CN206600385U (zh) * 2017-02-27 2017-10-31 李激初 离合器控制机构及其应用的内变速器

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9409844D0 (en) * 1994-05-17 1994-07-06 Sturmey Archer Ltd An epicyclic change gear system
JP3142247B2 (ja) * 1997-05-08 2001-03-07 株式会社シマノ 自転車用内装変速ハブ
US6607465B1 (en) * 2000-03-10 2003-08-19 Shimano, Inc. Bicycle hub transmission with a guiding member for a sun gear
CN2604335Y (zh) * 2003-02-11 2004-02-25 日驰企业股份有限公司 一种改进的内变速器轮毂轴及其具有其轮毂的内变速器
TWI236445B (en) * 2003-10-21 2005-07-21 Sun Race Sturmey Archer Inc Transmission hub structure of bicycle for rotary gear shift
CN201254436Y (zh) * 2008-07-10 2009-06-10 川方企业股份有限公司 绞车离合装置
KR100954300B1 (ko) * 2010-02-09 2010-04-22 (주)엠비아이 자전거 속도변환 보조장치
TWI542506B (zh) * 2014-12-12 2016-07-21 Univ Nat Yunlin Sci & Tech Bicycle five speed inner speed change mechanism
CN204878704U (zh) * 2015-08-18 2015-12-16 李激初 一种多挡变速器及其应用的中心轮棘爪安装结构

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN201021345Y (zh) * 2007-01-22 2008-02-13 福隆尖端科技股份有限公司 自行车的内变速器
US20100160109A1 (en) * 2008-12-24 2010-06-24 Sun Race Sturney Archer, Inc. Fixed gear internal gear hub
JP2012066723A (ja) * 2010-09-24 2012-04-05 Ntn Corp 回生機構を備えた電動補助自転車
CN202827982U (zh) * 2012-04-23 2013-03-27 谢定义 一种自行车内变速装置
CN103569306A (zh) * 2013-11-19 2014-02-12 李激初 自行车内变速器
CN204056187U (zh) * 2014-08-15 2014-12-31 李激初 一种自行车内变速器
CN206600385U (zh) * 2017-02-27 2017-10-31 李激初 离合器控制机构及其应用的内变速器

Also Published As

Publication number Publication date
CN108506368B (zh) 2023-12-22
TWI658964B (zh) 2019-05-11
CN108506368A (zh) 2018-09-07
TW201831803A (zh) 2018-09-01

Similar Documents

Publication Publication Date Title
KR100954300B1 (ko) 자전거 속도변환 보조장치
KR101782895B1 (ko) 자전거 변속허브
CN207315899U (zh) 离合器控制机构及其应用的内变速器
WO2016104564A1 (ja) 自転車用ドライブユニット
EP0795460B1 (en) Hub bicycle transmission
TWI532632B (zh) 內齒輪轂
WO2015154402A1 (zh) 电动自行车轮毂电机
TW200528335A (en) Internal speed changing hub for a bicycle
KR20180127231A (ko) 자전거용 다단기어 변속모터
WO2018153117A1 (zh) 离合器控制机构及其应用的内变速器
CN107244378B (zh) 一种三挡内变速器
TWI724652B (zh) 自行車變速裝置
WO2015154407A1 (zh) 离合器装置
TW201620781A (zh) 自行車三速內變速機構
CN106476979B (zh) 一种可实现快速启动的自行车双轮驱动装置
KR20140102592A (ko) 자전거용 무단 변속 장치
TWI638953B (zh) Built-in shifting mechanism for medical aids
TWI574885B (zh) With three speed shift function of the integrated variable speed gear motor
TWM527393U (zh) 自行車之無彈性件磁性花轂結構
US6401895B1 (en) Freewheeling hub device for a bicycle
TW201514058A (zh) 二輪載具結構（三）
TW201514057A (zh) 二輪載具結構（二）
KR20080048897A (ko) 유성 기어식 변속기와 그것을 이용한 차량
KR20030067016A (ko) 자전거의 추진장치
CN210126391U (zh) 可调偏心自行车轮毂离合结构

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: 17898101

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

32PN Ep: public notification in the ep bulletin as address of the adressee cannot be established

Free format text: NOTING OF LOSS OF RIGHTS PURSUANT TO RULE 112(1) EPC (EPO FORM 1205 DATED 27/01/2020)

122 Ep: pct application non-entry in european phase

Ref document number: 17898101

Country of ref document: EP

Kind code of ref document: A1