WO2020052434A1

WO2020052434A1 - Automatic speed-changing hub

Info

Publication number: WO2020052434A1
Application number: PCT/CN2019/102981
Authority: WO
Inventors: 王晓鸿; 胡京城; 武志国; 孙浙勇
Original assignee: 昆山唐泽新能源科技有限公司
Priority date: 2018-09-12
Filing date: 2019-08-28
Publication date: 2020-03-19
Also published as: CN108974243A; CN108974243B

Abstract

An automatic speed-changing hub (100), comprising: a hub shell (61); a hub shaft (51) used as a support and mounting structure; and at least two planetary gear sets (1, 2) mounted on the hub (51), different planetary gear sets (1, 2) outputting different rotational speed to the hub shell (51). Sun gears (10, 20), planetary gears (101, 201) or ring gears (13, 23) of adjacent planetary gear sets (1, 2) are not nested in the radial direction. A transmission part (71) is used for connecting the adjacent planetary gear sets (1, 2). The present automatic speed-changing hub features small volume, automatic speed change, easy maintenance and and an aesthetically pleasing external appearance.

Description

一种自动变速花鼓Automatic variable speed hub

技术领域Technical field

本发明属于自行车领域，特别涉及对变速花鼓的改进。The invention belongs to the field of bicycles, and particularly relates to improvement of a variable speed hub.

背景技术Background technique

现有的手动内三速变速花鼓***包括内三速花鼓、变速线、变速推杆、调速转把。以公开号为CN106114747A名称为“一种自行车用三级变速驱动装置”的专利为例，其至少存在以下问题：The existing manual internal three-speed variable-speed hub system includes an internal three-speed hub, a speed change line, a variable speed putter, and a speed control handle. Taking the patent whose publication number is CN106114747A as "a three-stage variable speed drive device for bicycles" as an example, it has at least the following problems:

花鼓内设置的用于变速的多组行星齿轮组，为了上一级行星齿轮组和下一级行星齿轮组之间传动，行星齿轮组在轴向上靠近不同行星齿轮组之间的行星架与齿环之间径向嵌套；并且变速花鼓的挡位越多嵌套的层级也就越多；嵌套造成了花鼓的直径增大从而导致其整体体积变大。A plurality of planetary gear sets for shifting are arranged in the hub. For the transmission between the upper planetary gear set and the lower planetary gear set, the planetary gear set is axially close to the planet carrier between different planetary gear sets and The gear rings are radially nested; and the more gears the gear hub has, the more nesting levels it has; the nesting causes the diameter of the hub to increase and its overall volume to become larger.

同时上述变速花鼓行星齿轮组通常都在花鼓输入速度的基础上做增速，使用行星架作为动力输入端齿环作为输出端，也就意味着升档以行星齿轮组的对花鼓壳体的转速输出逐渐提高。为了做到较高的速比，需要将行星齿轮组的直径设置的较大，并且速比越高最高速的行星齿轮组的直径也就越大，造成了高速比无法与小直径的行星齿轮组兼顾的问题。不能自动切换变速档位，需要人工调速。虽然花鼓的行星齿轮组能够进行速比转换，但行星齿轮组与花鼓之间的离合结合与分离需要人工触发；通常，在花鼓轴内设置一能够轴向滑移的推杆，该推杆轴向滑移到不同的位置即激发不同挡位的离合结合或分离，从而实现不同挡位的行星齿轮组驱动花鼓壳体。所述推杆被变速线牵引，变速线连接至调速转把上，从而可通过调速转把控制挡位。At the same time, the above-mentioned variable-speed hub planetary gear sets usually increase speed based on the hub input speed, and use the planet carrier as the power input end ring gear as the output end, which means that the upshift takes the planetary gear set's rotation speed to the hub housing. The output gradually increases. In order to achieve a higher speed ratio, the diameter of the planetary gear set needs to be set larger, and the higher the speed ratio, the larger the diameter of the highest-speed planetary gear set becomes, the higher the speed ratio cannot be compared with the planetary gear with a small diameter. Groups take into account issues. Can't switch gears automatically, need manual speed adjustment. Although the hub gear's planetary gear set can perform speed ratio conversion, the clutch coupling and separation between the planetary gear set and the hub require manual triggering; usually, a putter capable of axial sliding is provided in the hub shaft, and the putter shaft Sliding to different positions stimulates the clutch combination or separation of different gears, so that the planetary gear sets with different gears can drive the hub shell. The push rod is pulled by a speed change line, and the speed change line is connected to the speed adjusting handle, so that the gear can be controlled by the speed adjusting handle.

调速转把占用车把手的手握空间，外露的变速线和调速转把影响整车美观。The speed-adjusting handle occupies the space of the handlebar of the handlebar, and the exposed transmission line and speed-adjusting handle affect the beauty of the vehicle.

花鼓内需要延时出与所述变速线配合的变速推杆等部件，导致内部构件布局不尽合理，整车装配比较繁琐，对整车安装精度要求高。The hub needs to delay the production of components such as the variable speed putter that cooperates with the speed change line, resulting in unreasonable internal component layout, tedious assembly of the vehicle, and high requirements for vehicle installation accuracy.

整个***过于复杂，变速推杆和变速线由于外漏容易被损坏、变速线易老化，导致功能失效，需要定期维护。The entire system is too complicated. The shifting putter and the shifting line are easily damaged due to external leakage, and the shifting line is prone to aging, resulting in functional failure and requiring regular maintenance.

发明内容Summary of the Invention

本发明的目的在于解决上述技术问题。本发明的目的之一、是为了解决所述现有技术中因不同行星齿轮组之间的行星架与齿环之间径向嵌套导致其花鼓直径增大的问题。为解决上述问题本发明采用的手段是在使用传动部在相邻的行星齿轮组之间传动，使得相邻行星齿轮组在轴向方向上分离，径向方向上没有嵌套。更为具体的，本发明提供一种自动变速花鼓包括：An object of the present invention is to solve the above technical problems. One of the objectives of the present invention is to solve the problem of increasing the hub diameter of the prior art due to the radial nesting between the planet carrier and the ring gear between different planetary gear sets. In order to solve the above-mentioned problem, the method adopted by the present invention is to use a transmission part to transmit between adjacent planetary gear sets, so that the adjacent planetary gear sets are separated in the axial direction and there is no nesting in the radial direction. More specifically, the present invention provides an automatic gear hub including:

花鼓壳体；Hub shell

作为支撑、安装结构的花鼓轴；Hub shaft as support and installation structure;

安装在所述花鼓轴上的至少两级行星齿轮组，不同所述行星齿轮组向花鼓壳体输出不同转速；At least two-stage planetary gear sets installed on the hub shaft, different planetary gear sets output different speeds to the hub housing;

相邻所述行星齿轮组的太阳轮或行星轮或齿环之间径向方向上不嵌套；There is no nesting in the radial direction between the sun gear or the planet gear or the ring gear of the adjacent planetary gear sets;

相邻所述行星齿轮组之间使用传动部连接。A transmission portion is connected between the adjacent planetary gear sets.

由于所述传动部的代替行星齿轮组之间自身的零件的传动关系，使得所述相邻的行星齿轮组的行星架、齿环、太阳轮之间避免了嵌套，从而使得花鼓的直径不因行星齿轮组的直径变大而变大。Because the transmission part replaces the transmission relationship between the parts of the planetary gear set itself, the nests of the planet carrier, the ring gear, and the sun gear of the adjacent planetary gear set are avoided, so that the diameter of the hub is not It becomes larger as the diameter of the planetary gear set becomes larger.

本发明的目的之二是为了提高变速花鼓的综合变速比。为了达到该目的在花鼓内部设置第一行星齿轮组和第二行星齿轮组；Another object of the present invention is to improve the overall gear ratio of the gear hub. In order to achieve this purpose, a first planetary gear set and a second planetary gear set are provided inside the hub;

第一行星齿轮组的行星架与第二行星齿轮组的齿环通过所述传动部连接；The planet carrier of the first planetary gear set and the ring gear of the second planetary gear set are connected through the transmission part;

所述第一、第二行星齿轮组齿环或第二行星齿组的行星架用于驱动所述花鼓壳体；The ring gears of the first and second planetary gear sets or the planet carriers of the second planetary gear set are used to drive the hub shell;

离合组件，用于选择第一、第二行星齿轮组齿环或第二行星齿组的行星架驱动所述花鼓壳体。The clutch assembly is used for selecting the ring gear of the first or second planetary gear set or the planet carrier of the second planetary gear set to drive the hub housing.

所述第一行星齿轮组的行星架接入源动力，由于所述第二行星齿轮组的齿环与所述行星架通过传动部连接，使得第二行星齿轮组的齿环作为输入端，而第二行星齿轮组的行星架作为输出时其转速下降。在离合组件选择所述行星架驱动花鼓壳体时，花鼓壳体的转速比源动力的转速低，即在源动力的转速的基础上进一步降低了转速，相对而言综合速比得到了提高。The planetary carrier of the first planetary gear set is connected to source power. Since the ring gear of the second planetary gear set is connected to the planetary carrier through a transmission portion, the ring gear of the second planetary gear set is used as an input end, and The speed of the planetary carrier of the second planetary gear set decreases as the output. When the planetary carrier is used to drive the hub housing for the clutch assembly, the rotational speed of the hub housing is lower than the rotational speed of the source power, that is, the rotational speed is further reduced based on the rotational speed of the source power, and the overall speed ratio is relatively improved.

本发明目的之三是提供一种能够自动变速的花鼓，其是通过离心离心离合组件实现的。离心离合组件包括：设置在第一行星齿轮组的齿环上在第一踏频以上结合的第一离心离合；设置在第二行星齿轮组的齿环上在第二踏频以上结合的第二离心离合；A third object of the present invention is to provide a hub capable of automatically changing speed, which is realized by a centrifugal centrifugal clutch assembly. The centrifugal clutch assembly includes: a first centrifugal clutch coupled to the ring gear of the first planetary gear set above the first cadence; a second centrifugal clutch coupled to the ring gear of the second planetary gear set and above the second cadence Centrifugal clutch

所述第二行星齿轮组，在踏频低于第二踏频时通过行星架驱动花鼓壳体；The second planetary gear set, when the cadence is lower than the second cadence, drives the hub housing through the planet carrier;

所述第二行星齿轮组，在踏频高于第二踏频小于第一踏频时所述第二离心离合结合，并通过齿环驱动花鼓壳体；The second planetary gear set is combined with the second centrifugal clutch when the cadence is higher than the second cadence and less than the first cadence, and the hub shell is driven by the ring gear;

所述第一行星齿轮组，在踏频高于第一踏频时第一离心离合结合，并通过齿环驱动花鼓壳体。The first planetary gear set is coupled with the first centrifugal clutch when the cadence is higher than the first cadence, and drives the hub housing through the ring gear.

在第二离心离合未结合时，所述花鼓被第二行星齿轮组的行星架驱动，其处于花鼓低档模式。所述第二离心离合结合时花鼓处于中档模式，所述第一离心离合结合时花鼓处于高档模式。所述第二离心离合在高于第二踏频时结合，第一离心离合在高于第一踏频时结合其结合的过程由踏频决定不需要手动操作。When the second centrifugal clutch is not coupled, the hub is driven by the planet carrier of the second planetary gear set, which is in the hub low gear mode. The hub is in a mid-range mode when the second centrifugal clutch is combined, and the hub is in a high-end mode when the first centrifugal clutch is combined. The second centrifugal clutch is combined when the frequency is higher than the second cadence, and the process of combining the first centrifugal clutch when the frequency is higher than the first cadence is determined by the cadence without manual operation.

本发明目的之四是改进现有的离合结构使其能够随行星齿轮组转动自动结合或脱离。离心离合包括：离心块、离合片、棘爪和棘轮环；The fourth object of the present invention is to improve the existing clutch structure so that it can automatically engage or disengage as the planetary gear set rotates. Centrifugal clutch includes: centrifugal block, clutch plate, pawl and ratchet ring;

棘轮环，用于与所述棘爪啮合时向花鼓壳体输出动力；A ratchet ring for outputting power to the hub shell when engaging with the pawl;

离合结合时，离心块驱动离合片径向转动释放棘爪与棘轮环啮合；When the clutch is coupled, the centrifugal block drives the clutch to rotate radially to release the pawl to engage with the ratchet ring;

离合分离时，棘轮环的分离部转动迫使所述棘爪与棘轮环强制脱离。When the clutch is disengaged, the separation part of the ratchet ring is rotated to force the pawl to forcibly disengage from the ratchet ring.

可以看出离心块转动时驱动离合片释放所述棘爪，从而使得离合结合，并且棘轮环的分离部可以使得棘爪强制脱开。It can be seen that when the centrifugal block rotates, the clutch plate is driven to release the pawl, so that the clutch is coupled, and the separation part of the ratchet ring can forcibly disengage the pawl.

在优选的实施例中，所述棘轮环的分离部为径向向内延申的突起部，离合分离时所述分离部超越并压迫所述棘爪回缩。In a preferred embodiment, the separation portion of the ratchet ring is a protrusion that extends radially inward, and the separation portion oversteps and compresses the pawl to retract when the clutch is disengaged.

在优选的实施例中，棘轮环可以是独立的部件也可以是与花鼓壳体一体设置。In a preferred embodiment, the ratchet ring may be a separate component or may be integrally provided with the hub housing.

在优选的实施例中，所述花鼓内设置用于与棘轮环外齿啮合的固定齿环，所述固定齿环与花鼓固定连接或一体设置，所述棘轮环的棘齿在离合结合时与所述及棘爪啮合。In a preferred embodiment, a fixed toothed ring for meshing with the external teeth of the ratchet ring is provided in the hub, the fixed toothed ring is fixedly connected or integrally provided with the hub, and the ratchet teeth of the ratchet ring and The and pawl engage.

在优选的实施例中，所述离心块设置在所述齿环上的安装轴，离合结合时离心块绕所述安装轴转动时带动所述离合片径向转动；In a preferred embodiment, the centrifugal block is provided on a mounting shaft on the ring gear, and when the centrifugal block is rotated around the mounting shaft when the clutch is coupled, the clutch plate is caused to rotate radially;

所述离合片包括一棘爪收容槽，所述棘爪被部分地收容在所述棘爪收容槽；The clutch plate includes a pawl receiving groove, and the pawl is partially received in the pawl receiving groove;

离合片径向转动使得棘爪收容槽释放棘爪从初始位置转换到与所述花鼓壳体的驱动部啮合的位置。The clutch piece rotates radially so that the pawl receiving groove releases the pawl from the initial position to a position that engages with the driving part of the hub housing.

在优选的实施例中，所述第二行星齿轮组的行星架通过棘爪与所述花鼓壳体啮合。In a preferred embodiment, the planet carrier of the second planetary gear set is engaged with the hub housing by a pawl.

在优选的实施例中，所述传动部为套设在花鼓轴径向***的传动套筒，所述第二行星齿轮组和第一行星齿轮组的齿环设置与所述传动套筒连接的连接部。In a preferred embodiment, the transmission portion is a transmission sleeve sleeved on the radial periphery of the hub shaft, and the ring gears of the second planetary gear set and the first planetary gear set are connected to the transmission sleeve. Connection section.

在优选的实施例中，所述第一行星齿轮组与第二行星齿轮组互为镜像设置。In a preferred embodiment, the first planetary gear set and the second planetary gear set are mirror images of each other.

在优选的实施例中，所述离心块通过一驱动部与所述离合片连接；所述离心块与一复位件连接，离合分离时复位件驱动离心块和离合片反向转动。所述驱动部为与所述离合片配接的驱动杆，所述离合片上设置与所述驱动杆配接的开口，所述驱动杆部分的收容在所述开口内并通过开口驱动所述离合片转动。In a preferred embodiment, the centrifugal block is connected to the clutch plate through a driving part; the centrifugal block is connected to a reset member, and the reset member drives the centrifugal block and the clutch plate to rotate in reverse when the clutch is separated. The driving part is a driving rod mated with the clutch plate, and an opening mating with the driving rod is provided on the clutch plate, and the driving rod part is received in the opening and drives the clutch through the opening. The tablet rotates.

在优选的实施例中，所述复位件为设置在离心块安装轴上的扭簧，第一离心离合分离时踏频低于第一踏频第一离合组件的扭簧驱动离心块绕安装轴反向转动；第二离心离合分离时踏频低于第二踏频第二离合组件的扭簧驱动离心块绕安装轴反向转动。In a preferred embodiment, the resetting member is a torsion spring provided on the mounting shaft of the centrifugal block, and the torsion spring with the lower cadence of the first centrifugal clutch when the first centrifugal clutch is separated is driven around the mounting shaft by the torsion spring. Reverse rotation; when the second centrifugal clutch is disengaged, the torsion spring driven by the torsion spring of the second clutch assembly of the second centrifugal clutch rotates in the reverse direction about the installation axis.

在优选的实施例中，所述离合片包括一棘爪收容槽，所述棘爪被部分地收容在所述棘爪收容槽；离合结合时所述棘爪收容槽释放棘爪从初始位置转换到与所述花鼓壳体的驱动部啮合的位置。In a preferred embodiment, the clutch piece includes a pawl receiving groove, and the pawl is partially received in the pawl receiving groove; when the clutch is coupled, the pawl receiving groove releases the pawl to switch from the initial position To the position where it engages with the drive part of the hub housing.

在优选的实施例中，所述棘爪包括一弧形支撑部，所述弧形支撑部的背部设置有弹簧槽，一轴向固定弹簧穿过所述弹簧槽将其轴向固定在所述齿环上；所述弹簧压迫所述弧形支撑部的背部使得棘爪总是趋于远离所述棘爪收容槽；所述离合结合时，离合片转动到所述棘爪能够脱离所述收容槽的脱离位置，所述棘爪在弹簧的作用下从初始位置弹出，并与花鼓壳体的驱动部啮合。In a preferred embodiment, the pawl includes an arc-shaped support portion, a spring groove is provided on the back of the arc-shaped support portion, and an axially fixed spring passes through the spring groove to axially fix the spring groove in the spring groove. On the ring gear; the spring presses the back of the arc-shaped support portion so that the pawl always moves away from the pawl receiving groove; when the clutch is coupled, the clutch plate is rotated to the pawl to be able to disengage from the receiving In the disengaged position of the groove, the pawl is ejected from the initial position under the action of the spring, and is engaged with the driving part of the hub shell.

本发明的有益技术效果至少包括以下几点：1.通过传动部在相邻行星齿轮组在轴向方向上分离避免径向嵌套减小了花鼓的直径和体积。The beneficial technical effects of the present invention include at least the following points: 1. Separation of adjacent planetary gear sets in the axial direction by the transmission portion to avoid radial nesting reduces the diameter and volume of the hub.

2.通过选择所述使用第二行星齿轮组的行星架驱动花鼓壳体，即在源动力的转速的基础上进一步降低了转速，变速花鼓的综合速比得到了提高。2. By selecting the planetary carrier that uses the second planetary gear set to drive the hub housing, that is, the speed is further reduced based on the speed of the source power, and the overall speed ratio of the variable speed hub is improved.

3.第一、第二离心力离合在不同踏频下自动结合不需要人工操作换挡。3. The first and second centrifugal force clutches are automatically combined under different cadences without the need to manually shift gears.

4.消除了原有内三速变速花鼓的指拨***(变速线、变速推杆、调速转把)，可使自行车在外观上有进一步的改善。4. Elimination of the original inner three-speed shifting hub system (shift line, shifting putter, speed adjustment handle), which can further improve the appearance of the bicycle.

5.消除了变速推杆等部件结构更合理，整车装配更简单改善了后轴回转运动的稳定性，提高了使用的可靠性和安全性。5. Eliminated the more reasonable structure of components such as variable speed putter, simpler vehicle assembly, improved the stability of rear axle rotation, and improved the reliability and safety of use.

6.变速装置安装在花鼓壳内部无需变速线，经过多层密封保护避免暴露在外界，因此雨水、灰尘、油垢等均无法进入，也避免了太阳的暴晒与风雨的侵蚀，故无需定期保养，实现了免保养、精密、耐用、轻巧等优点。6. The gear shifting device is installed inside the hub shell without the need for a speed changing cable. It is protected from exposure to the outside through multiple layers of sealing protection, so rain, dust, grease, etc. cannot be entered, and the sun and wind and rain are avoided, so regular maintenance is not required. Achieve the advantages of maintenance-free, precision, durable, lightweight and so on.

附图说明BRIEF DESCRIPTION OF THE DRAWINGS

图1是自动内三速花鼓剖面结构示意图，其中行星齿轮组以及离合组件以模块的形式表示。FIG. 1 is a schematic structural sectional view of an automatic internal three-speed hub, in which a planetary gear set and a clutch assembly are represented in the form of a module.

图2是自动内三速花鼓剖面结构示意图。FIG. 2 is a schematic structural cross-sectional view of an automatic internal three-speed hub.

图3是自动内三速花鼓剖面结构示意图，其中省略了花鼓的壳体。FIG. 3 is a schematic cross-sectional structure diagram of an automatic internal three-speed hub, in which the hub shell is omitted.

图4是离心离合的俯视结构示意图。FIG. 4 is a schematic plan view of a centrifugal clutch.

图5是图4中省略了离心块和离合片的俯视结构示意图。FIG. 5 is a schematic plan view of the structure in which the centrifugal block and the clutch plate are omitted in FIG. 4.

图6是图4中离心离合离合片俯视结构示意图。FIG. 6 is a schematic plan view of the centrifugal clutch clutch plate in FIG. 4.

图7是离心离合的剖面结构示意图。Fig. 7 is a schematic sectional structural view of a centrifugal clutch.

图8是花鼓立体结构示意图，并展示了1/4剖面。Fig. 8 is a schematic view of the three-dimensional structure of the hub and shows a 1/4 cross section.

具体实施方式detailed description

请参照图1至图8所示的自动变速花鼓示意图。其中在图1中为了简便说明技术要点变速花鼓内的行星齿轮组B被简化成一个模块。传动部T在相邻的行星齿轮组B之间传动，使得相邻行星齿轮组B在轴向方向上分离，径向方向Y上没有嵌套。更为具体的，自动变速花鼓包括：Please refer to the schematic diagrams of the automatic shift hub shown in FIGS. 1 to 8. Among them, the planetary gear set B in the shift hub is simplified into a module for the sake of simplicity in describing the technical points. The transmission part T is transmitted between the adjacent planetary gear sets B, so that the adjacent planetary gear sets B are separated in the axial direction, and there is no nesting in the radial direction Y. More specifically, the automatic shift hub includes:

花鼓壳体S，作为花鼓的动力输出端通过轮辐与车轮连接，花鼓壳体被行星齿轮组B驱动；The hub shell S, as the power output end of the hub, is connected to the wheels through spokes, and the hub shell is driven by the planetary gear set B;

作为支撑、安装结构的花鼓轴A用于将花鼓安装在车架等固定结构上，其用于支撑车轮对花鼓的压力并将压力传递到车架上，同时花鼓轴还可以作为行星齿轮组的一部分构件，例如可在花鼓轴上一体的设置太阳轮，行星齿轮组安装在所述花鼓轴上；The hub shaft A as a support and mounting structure is used to install the hub on a fixed structure such as a frame. It is used to support the wheel's pressure on the hub and transmit the pressure to the frame. At the same time, the hub shaft can also be used as a planetary gear set. Some components, for example, a sun gear may be integrally provided on the hub shaft, and the planetary gear set is mounted on the hub shaft;

安装在所述花鼓轴A上的至少两级行星齿轮组B，不同所述行星齿轮组B向花鼓壳体S输出不同转速；行星齿轮组的源动力来自飞轮，进一步来自用户的踩踏力，飞轮通过传动结构将动力传递至不同级的行星齿轮组，经过行星齿轮组的变速再将不同的转速输出到花鼓壳体上。At least two-stage planetary gear sets B mounted on the hub shaft A, different planetary gear sets B output different rotation speeds to the hub housing S; the source power of the planetary gear sets comes from the flywheel, and further from the pedaling force of the user, the flywheel The power is transmitted to the planetary gear sets of different stages through the transmission structure, and then the different speeds are output to the hub shell through the speed change of the planetary gear set.

在图1中设置了四级行星齿轮组B，行星齿轮组之间的使用传动部T连接；显然可以设置更多或更少级数的行星齿轮组。相邻所述行星齿轮组B的太阳轮或行星轮或齿环之间径向方向上不嵌套；这里径向嵌套是指行星齿轮组之间为了传动会将其一部分结构(通常是行星架的部分结构)沿着轴向延申到相邻行星齿轮组B的内部，为了收容该延申结构不得不将相邻行星齿轮组的结构(通常是齿环)套设在所述延申结构的径向外侧造成相邻行星齿轮组的直径增大。A four-stage planetary gear set B is provided in FIG. 1, and the planetary gear sets are connected using a transmission portion T; obviously, more or fewer planetary gear sets may be provided. There is no nesting in the radial direction between the sun gear or the planet gear or the ring gear of the adjacent planetary gear set B. Here, radial nesting means that a part of the structure (usually a planet Part of the structure of the frame) is extended to the inside of the adjacent planetary gear set B along the axial direction. In order to accommodate the extended structure, the structure of the adjacent planetary gear set (usually a ring gear) must be set on the extension. The radially outer side of the structure causes an increase in the diameter of adjacent planetary gear sets.

在图1中所述传动结构围绕花鼓轴设置，套设再花鼓轴A上；传动部T还可以是与所述轴套不接触的杆状、板状、柱状等等效替换结构。所述齿轮组也不仅限于图示中的四组，根据变速级数的需求可以设置更多的齿轮组。In FIG. 1, the transmission structure is arranged around the hub shaft, and is sleeved on the hub shaft A. The transmission portion T may also be an equivalent replacement structure such as a rod shape, a plate shape, or a column shape that is not in contact with the sleeve. The gear sets are not limited to the four sets shown in the figure, and more gear sets can be provided according to the requirements of the number of shift stages.

由于所述传动部T的代替行星齿轮组B之间自身的零件嵌套的传动关系，使得所述相邻的行星齿轮组B的行星架、齿环、太阳轮之间避免了嵌套，也能够完成传动的要求，从而使得花鼓的直径不因行星齿轮组的直径变大而变大。Because the transmission portion T replaces the nested transmission relationship between the parts of the planetary gear set B, the nesting between the planet carriers, ring gears, and sun gears of the adjacent planetary gear set B is avoided, and The requirements of the transmission can be completed, so that the diameter of the hub does not increase as the diameter of the planetary gear set becomes larger.

以下结合图2-8说明自动变速花鼓的具体结构以内三速自动变速花鼓，来说明自动变速花鼓的技术原理和技术进步。The specific structure of the automatic shift hub is described below with reference to FIGS. 2-8. The three-speed automatic shift hub is used to illustrate the technical principles and technical progress of the automatic shift hub.

内三速花鼓包括两级行星齿轮组，使用中置的行星架11、21作为驱动部件，并设置离心离合根据踏频切换不同的行星齿轮组输出,花鼓壳体61获得不同的转速，由于离心离合1、2的存在，因此整个过程是自动的。The inner three-speed hub consists of a two-stage planetary gear set. It uses the central

planetary carriers

11 and 21 as drive components, and sets the centrifugal clutch to switch the output of different planetary gear sets according to the cadence. The hub shell 61 obtains different speeds. Clutches 1 and 2 exist, so the whole process is automatic.

自动内三速花鼓100包括:起到支撑安装作用的花鼓轴51；作为动力输出的花鼓壳体61；安装在所述花鼓轴51上的，第一行星齿轮组1、第二行星齿轮组2；所述第一行星齿轮组的行星架11(以下简称第一行星架11)作为动力输入端，第一行星架11与第二行星齿轮组的齿环(以下简称第二齿环23)通过所述传动部71连接；该传动部71为一传动轴套装置套71设在所述花鼓轴51上。所述第一、第二行星齿轮组齿环(以下简称第一、第二齿环)或第二行星齿组的行星架(以下简称第二行星架)用于驱动所述花鼓壳体61。The automatic internal three-speed hub 100 includes: a hub shaft 51 supporting and installing; a hub housing 61 serving as a power output; and a first planetary gear set 1 and a second planetary gear set 2 mounted on the hub shaft 51 ; The planet carrier 11 of the first planetary gear set (hereinafter referred to as the first planet carrier 11) serves as a power input end, and the first planet carrier 11 and the ring gear of the second planetary gear set (hereinafter referred to as the second ring gear 23) pass through The transmission portion 71 is connected; the transmission portion 71 is a transmission shaft sleeve device sleeve 71 provided on the hub shaft 51. The first and second planetary gear sets of the ring gear (hereinafter referred to as the first and second ring gears) or the planetary carrier of the second planetary gear set (hereinafter referred to as the second planetary carrier) are used to drive the hub housing 61.

离合组件，用于选择第一、第二齿环13、23或第二行星架21驱动所述花鼓壳体61。第一齿环13上设置有在第一踏频以上结合的第一离心离合，第二行星齿轮组2上设置有在第二踏频以上结合的第二离心离合；所述第一或第二离心离合上包括离心块19、29、离合片17、27、棘爪15、25和棘轮环16、26，离合结合时离心块驱动离合片17、27径向转动，所述离合片17、27转动将被锁住的棘爪15、25释放，棘爪15、25与花鼓壳体由棘轮环16、26、和固定齿环18、28组成的驱动部啮合。驱动部可与花鼓壳体为一体件。The clutch assembly is used to select the first and second ring gears 13 and 23 or the second planet carrier 21 to drive the hub housing 61. The first ring gear 13 is provided with a first centrifugal clutch coupled above the first cadence, and the second planetary gear set 2 is provided with a second centrifugal clutch coupled above the second cadence; the first or second The centrifugal clutch includes

centrifugal blocks

19, 29,

clutch pieces

17, 27,

pawls

15, 25, and ratchet

rings

16, 26. When the clutch is coupled, the centrifugal block drives the

clutch pieces

17, 27 to rotate radially, and the

clutch pieces

17, 27 Rotation releases the locked

pawls

15, 25, which are engaged with the drive part of the hub housing composed of ratchet rings 16, 26, and fixed toothed rings 18, 28. The driving part may be integrated with the hub housing.

所述第一行星齿轮组1、第二行星齿轮组2的太阳轮10、20(以下简称第一、第二太阳轮)安装在所述花鼓轴51上，或与所述花鼓轴51一体设置，在本发明中第一行星齿轮组1的太阳轮10与花鼓轴51固定安装。其太阳轮10、20在行星齿轮101、201转动过程中始终固定在花鼓轴51上不转动。The sun gears 10 and 20 of the first planetary gear set 1 and the second planetary gear set 2 (hereinafter referred to as the first and second sun gears) are installed on the hub shaft 51 or integrated with the hub shaft 51 In the present invention, the sun gear 10 of the first planetary gear set 1 and the hub shaft 51 are fixedly mounted. The sun gears 10 and 20 of the sun gears 10 and 20 are always fixed on the hub shaft 51 during rotation of the

planetary gears

101 and 201 and do not rotate.

第一行星齿轮架11包括飞轮安装部43和密封部111。所述飞轮41安装部43内部设置滚道431，该滚道431用于部分收容设置在玉押42和行星架11之间的滚球113，玉押42起到轴向固定所述行星齿轮架11的作用，亦同时固定所述花壳体61轴向位置。飞轮安装部43的外周侧与飞轮连接，骑行动力通过飞轮41传递到所述第一行星齿轮架11。The first planetary carrier 11 includes a flywheel mounting portion 43 and a sealing portion 111. The flywheel 41 mounting portion 43 is provided with a raceway 431 inside. The raceway 431 is used to partially accommodate the ball 113 provided between the jade 42 and the planet carrier 11. The jade 42 plays an axial role in fixing the planet gear carrier. The function of 11 also fixes the axial position of the flower casing 61 at the same time. The outer peripheral side of the flywheel mounting portion 43 is connected to the flywheel, and the riding force is transmitted to the first planetary carrier 11 through the flywheel 41.

所述密封部111在径向方向Y延申，其被所述花鼓壳体61竖直方向的延伸部115包围，密封部的边缘设置有滚道112，花鼓壳体的最右侧设置有滚道环116，滚道环116与所述密封部的滚道112共同收容滚球114，所述第一行星齿轮组1通过滚球114支撑花鼓壳体。The sealing portion 111 extends in the radial direction Y and is surrounded by the vertical extension 115 of the hub housing 61. The edge of the sealing portion is provided with a raceway 112, and the roller on the rightmost side of the hub housing is provided with a roller. The raceway ring 116, the raceway ring 116 and the sealway 112 of the sealing portion jointly receive the ball 114, and the first planetary gear set 1 supports the hub housing through the ball 114.

所述密封部111的内侧安装星轮轴102(参照图8)，星轮101安装在所述星轮轴102上，第一行星架11远离所述飞轮安装部43的一端设置一传动轴套连接部114，该连接部114与套设在花鼓轴上的传动轴套连接71，两者可使用花键或固定连接的方式。A star wheel shaft 102 (refer to FIG. 8) is mounted on the inner side of the sealing portion 111, a star wheel 101 is mounted on the star wheel shaft 102, and a transmission shaft sleeve connection portion is provided at an end of the first planet carrier 11 away from the flywheel mounting portion 43. 114. The connecting portion 114 is connected 71 with a transmission sleeve sleeved on the hub shaft, and the two can be splined or fixedly connected.

第一齿环13呈宝塔状，其包括与所述星轮101连接的啮合部12，和用于安装第一离心离合的离合安装部14，离心离合在结合时与所述离合安装部14径向外侧花鼓壳体驱动部16、18或花鼓壳体61连接。应当注意的是第一齿环13不是直接安装在所述花鼓轴51上的而是通所述离心离合安装部14径向内侧的收容腔套设在所述传动轴套上，该齿环的收容腔200和行星架上的外壁均为圆柱状，所述第一齿环13与所述传动轴套71无连接可相互自由转动。The first ring gear 13 has a pagoda shape, and includes an engaging portion 12 connected to the star wheel 101, and a clutch installation portion 14 for installing a first centrifugal clutch. The outer hub

housing driving portions

16 and 18 or the hub housing 61 are connected. It should be noted that the first ring gear 13 is not directly installed on the hub shaft 51 but is sleeved on the transmission shaft sleeve through a receiving cavity radially inward of the centrifugal clutch mounting portion 14. The receiving cavity 200 and the outer wall of the planet carrier are both cylindrical, and the first ring gear 13 and the transmission sleeve 71 can rotate freely without connection.

第二行星齿轮组2与第一行星齿轮组1为互为镜像结构。第二行星架21安装在所述花鼓轴51上，该行星架的主体部设置行星轮201。第二行星架21远离所述行星轮的一端用于驱动所述花鼓壳体61，第二行星架21过棘齿233与花鼓壳体61啮合。The second planetary gear set 2 and the first planetary gear set 1 are mirror images of each other. The second planet carrier 21 is mounted on the hub shaft 51, and a planetary wheel 201 is provided on the main body of the planet carrier. An end of the second planet carrier 21 remote from the planet wheel is used to drive the hub housing 61, and the second planet carrier 21 meshes with the hub housing 61 through ratchet teeth 233.

第二齿环23呈宝塔状，其包括与所述星201轮连接的啮合部22和用于安装第二离心离合的离合安装部24，离心离合在结合时与所述离合安装部24径向外侧花鼓壳体驱动部26、28连接。第二齿环23通过设置在离心离合安装部24径向内侧的收容腔300内壁(参照图8)作为与传动轴套71左侧端部连接的连接部；所述内壁上可设置与所述传动轴套连接的花键。The second ring gear 23 is in the shape of a pagoda, and includes an engaging portion 22 connected to the star 201 wheel and a clutch installation portion 24 for installing a second centrifugal clutch. The centrifugal clutch is radial to the clutch installation portion 24 when it is combined. The outer hub

housing drive sections

26, 28 are connected. The second ring gear 23 is an inner wall (refer to FIG. 8) of the receiving cavity 300 provided on the radially inner side of the centrifugal clutch mounting portion 24 as a connection portion connected to the left end portion of the transmission shaft sleeve 71; Spline for drive bushing connection.

第行星架11转动时通过传动轴套71驱动第二齿环23转动，第二行星架21被第二齿环23驱动。When the first planet carrier 11 rotates, the second ring gear 23 is driven to rotate by the transmission sleeve 71, and the second planet carrier 21 is driven by the second ring gear 23.

所述第一行星架11连接源动力，由于所述第二齿环23与所述行星架11通过传动轴套71连接，使得第二齿环作23为输入端，行星齿轮组的传动特性所致第二行星架21作为输出时其转速相对第二齿环23下降。第二行星架21与所述传动轴套71连接两者的转速相同。第一行星架11作为输入时，行星齿轮组的传动特性所致第一齿环13的转速大于行星架的转速。因此在所述第二行星架21、第二齿环23、第一齿环13分别与花鼓壳体啮合时对应的花鼓的转速分别为R1、R2、R3，并且R1<R2<R3。The first planetary carrier 11 is connected to source power. Since the second ring gear 23 and the planetary carrier 11 are connected through a transmission sleeve 71, the second ring gear 23 is used as an input end, and the transmission characteristics of the planetary gear set are affected. When the second planet carrier 21 is used as an output, its rotation speed is lowered relative to the second ring gear 23. The second planetary carrier 21 and the transmission shaft sleeve 71 are connected at the same rotation speed. When the first planet carrier 11 is used as an input, the rotation speed of the first ring gear 13 caused by the transmission characteristics of the planetary gear set is greater than the rotation speed of the planet carrier. Therefore, when the second planet carrier 21, the second ring gear 23, and the first ring gear 13 are respectively engaged with the hub housing, the rotation speeds of the corresponding hubs are R1, R2, R3, and R1 <R2 <R3.

申请人经过实验优化行星齿轮组的齿比，在离合组件选择所述第二行星架21驱动花鼓壳体时，花鼓壳体61的转速为所述传动轴套71转速的0.55倍，在选择所述第一齿环13驱动花鼓壳体时所述花鼓壳体的转速为传动轴套的1.36倍数，第二齿环的转速与传动轴套的转速相同即R1:R2:R3＝0.55:1:1.36,其综合速比R1:R3≈2.47,相对而言不带降速功能的三速花鼓综合速比为1.69，因此综合速比具有很大的提升能带来明显不同的骑行感受。The applicant optimized the gear ratio of the planetary gear set through experiments. When the second planet carrier 21 is selected to drive the hub housing by the clutch assembly, the rotation speed of the hub housing 61 is 0.55 times the rotation speed of the transmission shaft sleeve 71. When the first ring gear 13 drives the hub shell, the rotation speed of the hub shell is 1.36 times the transmission shaft sleeve, and the rotation speed of the second ring gear is the same as the rotation speed of the transmission shaft sleeve, ie, R1: R2: R3 = 0.55: 1: 1.36, its comprehensive speed ratio R1: R3 ≈ 2.47, relatively speaking, the comprehensive speed ratio of the three-speed hub without speed reduction function is 1.69, so the comprehensive speed ratio has a great improvement and can bring significantly different riding experience.

在骑行过程中第一行星架11被所述飞轮41驱动，第二齿环21和传动轴套71与所第一行行星架11同步转动。不论骑行者的踏频如何改变，上述三个部件均保持同步转动。而第一行星齿轮组1和第二行星齿轮组2的齿环13和第二行星齿轮组的行星架的转速分别为R1、R2、R3。所述转速分别对应低档、中档和高档。During riding, the first planet carrier 11 is driven by the flywheel 41, and the second ring gear 21 and the transmission sleeve 71 rotate synchronously with the planet carrier 11 of the first row. Regardless of how the rider's cadence changes, the three components described above keep rotating in sync. The rotational speeds of the ring gear 13 of the first planetary gear set 1 and the second planetary gear set 2 and the planetary carrier of the second planetary gear set are R1, R2, R3, respectively. The rotation speeds correspond to low gear, medium gear, and high gear, respectively.

离心离合再不同踏频下切换第一13、第二齿环23和第二行星架21，与花鼓壳体61的驱动关系完成低档、中档、高档换挡。所低档、中档和高档位的对应的花鼓壳体输出的转速分别为低速R1、中速R2和高速R3。离心离合换挡的临界踏频为第二踏频、第一踏频，低于所述第二踏频花鼓处于低档低速状态，大于等于第二踏频小于第一踏频花鼓处于中档中速状态，大于等于第一踏频花鼓处于高档高速状态。The centrifugal clutch switches the first 13, second ring gear 23, and second planetary carrier 21 at different cadences, and the driving relationship with the hub housing 61 completes low-, medium-, and high-end gear shifts. The rotation speeds output by the corresponding hub housings in the low gear, middle gear, and high gear are low speed R1, middle speed R2, and high speed R3, respectively. The critical cadence of the centrifugal clutch shift is the second cadence and the first cadence, which is lower than the second cadence hub in a low-speed and low-speed state, and equal to or greater than the second cadence is smaller than the first cadence hub in a medium-speed medium-speed state , Greater than or equal to the first cadence hub is in a high-grade high-speed state.

对于确定齿比的行星齿轮组所述离心离合结合时的临界转速是固定的，因此对于确定齿比的自行车牙盘和飞轮组合，所述离心离合的临界踏频也是确定的。本领域技术人员可以根据需要调整行星齿轮组的齿比或牙盘和飞轮的齿比来调整所述换档临界踏频。For the planetary gear set that determines the gear ratio, the critical speed when the centrifugal clutch is combined is fixed, so for the combination of the bicycle crank and flywheel that determines the gear ratio, the critical cadence of the centrifugal clutch is also determined. Those skilled in the art can adjust the gear shift critical cadence according to the needs of adjusting the gear ratio of the planetary gear set or the gear ratio of the crank disk and the flywheel.

花鼓自动升档过程按照不同的档位，骑行动力传输的路径也不同：The automatic upshift process of the hub according to different gears, the path of riding power transmission is also different:

低档时，骑行者的踏频小于第二踏频骑行动力从飞轮41输入，经过第一星架11传递传动轴套71再到第二齿环13，再从第二齿环13传递至第二行星架11上，最后到达花鼓壳体61。参照图中所示的箭头标识的路径，A->B->C->D->E->G->I->J。第二行星架21上设置与花鼓壳体61的驱动部233啮合的棘爪(驱动部和棘爪在下文中详细介绍)，通过该棘爪和驱动部233所述骑行动力被传递到花鼓壳体61上。由于在整个低档传动过程中，此时的踏频低于第二踏频，因此第一离心离合和第二离心离合都处于分离的状态，第一行星齿轮组1的第一齿环11和第二行星齿轮组2的第二齿环21处于无负载空转状态，因此花鼓壳61的输出的转速为R1。In low gear, the rider ’s cadence is less than the second cadence. Riding power is input from the flywheel 41, and the transmission sleeve 71 is transmitted to the second ring gear 13 via the first star carrier 11, and then transmitted from the second ring gear 13 to the first. The two planet carriers 11 finally reach the hub housing 61. Referring to the path indicated by the arrow shown in the figure, A-> B-> C-> D-> E-> G-> I-> J. The second planet carrier 21 is provided with a pawl (the driving part and the pawl will be described in detail below) that is engaged with the driving part 233 of the hub housing 61, and the riding force is transmitted to the hub case through the pawl and the driving part 233. Body 61. Because the cadence at this time is lower than the second cadence during the entire low-speed transmission, the first centrifugal clutch and the second centrifugal clutch are in a separated state. The first ring gear 11 and the first planetary gear set 1 Since the second ring gear 21 of the two planetary gear set 2 is in a no-load idling state, the output rotational speed of the hub shell 61 is R1.

中档时，骑行者的踏频大于第二踏频小于第一踏频，骑行经过传动轴套71传递到第二齿环23，通过第二轮组的行星齿离心离合到达壳体61，其动力传递的路径是A->B->C->D->E->F->G->H。由于骑行踏频大于第二踏频并小于第一踏频，所述第二离心离合结合，第二离心离合上的棘爪25与被花鼓壳体驱动部26、28啮合。第二行星齿轮组2的齿环23通过棘爪25驱动所述花鼓壳体61，花鼓壳体61的和第二行星齿轮组的齿环23同步转动，其转速为R2与所述传动轴套以及第一行星齿轮组的行星架的转速相同。此时由于花鼓壳体的转速为R2大于所述第二行星齿轮组行星架的转速，造成第二行星齿轮组行星架上的棘爪33与花鼓壳体驱动部233、234脱离，第二行星架21处于无负载空转状态。相应的踏频小于第一踏频，使得所述第一离心离合处于分离的状态，所述第一行星齿轮组1的齿环11空转，也即第一离心离合处于分离空转状态。In the mid-range, the cyclist's cadence is greater than the second cadence and less than the first cadence. The rider passes the transmission sleeve 71 to the second ring gear 23 and reaches the casing 61 through the centrifugal clutch of the planetary teeth of the second wheel set. The path of power transmission is A-> B-> C-> D-> E-> F-> G-> H. Since the riding cadence is greater than the second cadence and less than the first cadence, the second centrifugal clutch is combined, and the pawl 25 on the second centrifugal clutch is engaged with the driven

parts

26 and 28 of the hub housing. The ring gear 23 of the second planetary gear set 2 drives the hub housing 61 through the pawl 25. The hub housing 61 and the ring gear 23 of the second planetary gear set rotate synchronously at a speed of R2 and the transmission sleeve And the rotation speed of the planet carrier of the first planetary gear set is the same. At this time, since the rotation speed of the hub housing is R2 greater than the rotation speed of the planet carrier of the second planetary gear set, the pawl 33 on the planet carrier of the second planetary gear set is disengaged from the hub

housing driving parts

233 and 234, and the second planet The rack 21 is in a no-load idling state. The corresponding cadence is smaller than the first cadence, so that the first centrifugal clutch is in a separated state, and the ring gear 11 of the first planetary gear set 1 is idling, that is, the first centrifugal clutch is in a separated idling state.

高档时，骑行的踏频大于第一踏频，骑行动力从飞轮41输入传递到第一星星齿轮架11，通过第一离心离合传递到花鼓壳体62，其动力传递路径为A->B->C->D->E。由于踏频大于第一踏频，因此第一齿环13上的第一离心离合结合，第一离心离合上的棘爪15与花鼓壳体驱动部16、18啮合。第一齿环13通过棘爪15驱动所述花鼓壳体61，花鼓壳体61与第一行星齿轮的齿轮环13同步转动，其转速R3大于第二行星齿环23以及第二行星架21的转速。此时第二离心离合棘爪25与花鼓壳体驱动部26、28脱离，第二行星架21棘爪与花鼓壳体61驱动部233、234也脱离，所述第二行星齿环23、第二行星架21均处于空转状态。In high gear, the riding cadence is greater than the first cadence, and the riding power is transmitted from the flywheel 41 to the first star gear carrier 11 and transmitted to the hub housing 62 through the first centrifugal clutch. Its power transmission path is A-> B-> C-> D-> E. Since the cadence is greater than the first cadence, the first centrifugal clutch on the first ring gear 13 is combined, and the pawl 15 on the first centrifugal clutch is engaged with the hub

housing driving portions

16 and 18. The first ring gear 13 drives the hub housing 61 through the pawl 15. The hub housing 61 rotates synchronously with the gear ring 13 of the first planetary gear, and its rotation speed R3 is greater than that of the second planetary ring gear 23 and the second planetary carrier 21. Rotating speed. At this time, the second centrifugal clutch pawl 25 is disengaged from the hub

housing driving portions

26 and 28, and the second planet carrier 21 pawl is also disengaged from the hub housing 61 driving

portions

233 and 234. Both planet carriers 21 are in an idling state.

花鼓自动降档过程与升档动作相反，当踏频降低至低于第一踏频高于第二踏频时，第一离心离合分离，花鼓壳体61的速度下降第二离心离合结合降为中档，此时第一行星齿轮组1的齿环13和第二行星齿轮组的行星架21处于空转状态。当踏频降低至低于第二踏频，花鼓壳体的速度进一步下降第二离心离合分离第二行星架上的棘齿233与花鼓壳体啮合降为低速档，此时第一行星齿轮组1的齿环13和第二行星齿轮组2的齿环23均处于空转状态。第一离心离合分离驱动棘爪15与花鼓的驱动部16、18分离，第二离心离合分离驱动棘爪25与花鼓的驱动部26、28分离。The automatic downshift of the hub is opposite to the upshift. When the cadence is lower than the first cadence and higher than the second cadence, the first centrifugal clutch is separated, and the speed of the hub shell 61 is reduced. The second centrifugal clutch combination is reduced to In the middle gear, at this time, the ring gear 13 of the first planetary gear set 1 and the planet carrier 21 of the second planetary gear set are in an idling state. When the cadence is lower than the second cadence, the speed of the hub housing is further reduced. The second centrifugal clutch separates the ratchet teeth 233 on the second planetary carrier from engaging with the hub housing to a low speed. At this time, the first planetary gear set The ring gear 13 of 1 and the ring gear 23 of the second planetary gear set 2 are both in an idle state. The first centrifugal clutch and separation driving pawl 15 is separated from the

hub driving parts

16 and 18, and the second centrifugal clutch and separation driving pawl 25 is separated from the

hub driving parts

26 and 28.

低于第二踏频小于第一踏频时第二离心离合未结合时，所述花鼓被第二行星齿轮组的行星架驱动。高于第二踏频小于第一踏频所述第二离心离合结合时花鼓处于中档模式。高于第一踏频第一离心离合结合时花鼓处于高档模式。同时在中档和高档换挡时能够使得其他两档驱动棘爪与花鼓分离。因此花鼓的升降党过程完全由踏频的升降过程决定，不需要手动操作。When the second centrifugal clutch is not coupled when the second cadence is lower than the first cadence, the hub is driven by the planet carrier of the second planetary gear set. When the second centrifugal clutch is higher than the second cadence and is smaller than the first cadence, the hub is in a mid-range mode. When the first centrifugal clutch is higher than the first cadence, the hub is in a high-end mode. At the same time, the middle two and high gear shifts can separate the other two gear drive pawls from the hub. Therefore, the lifting party process of the hub is completely determined by the cadence lifting process, and no manual operation is required.

第一离心离合和第二离心离合的工作原理完全相同，两者的区别在于第一离心离合和第二离心离合结合和分离的临界踏频不同，所述不同的踏平对应自动变速花鼓不同的档位；同时花鼓壳体的驱动部工作远离也完全相同，仅存在尺寸或齿数上的不同。因此为了简要，以第一离心离合为例，说明离心离合和花鼓驱动部的工作原理。The working principle of the first centrifugal clutch and the second centrifugal clutch are completely the same. The difference between the two is that the critical cadence of the first centrifugal clutch and the second centrifugal clutch are different, and the different pedaling levels correspond to different automatic transmission hubs. Gear position; at the same time, the drive part of the hub shell is far from the same work, only there are differences in size or number of teeth. Therefore, for the sake of brevity, the first centrifugal clutch is taken as an example to explain the working principle of the centrifugal clutch and the hub driving unit.

第一离心离合上包括离心块19、离合片17、棘爪15和棘轮环16，离心块19、离合片17、棘爪15均安装在所述第一齿环13上。所述齿环13星轮啮合部12的直径大于离合安装部14的直径，在离合安装部14径向外侧，形成一环状***述棘爪15、离合片17和离心块19的空间。棘轮环16作为花鼓壳体驱动部的一部分安装在花鼓壳体61上，用于与所述棘爪15啮合时向花鼓壳体61输出动力。The first centrifugal clutch includes a centrifugal block 19, a clutch sheet 17, a pawl 15, and a ratchet ring 16. The centrifugal block 19, the clutch sheet 17, and the ratchet 15 are all mounted on the first ring gear 13. The diameter of the star wheel engaging portion 12 of the ring gear 13 is larger than the diameter of the clutch mounting portion 14. A radial space is formed outside the clutch mounting portion 14 radially to receive the pawl 15, the clutch plate 17 and the centrifugal block 19. The ratchet ring 16 is mounted on the hub housing 61 as a part of the driving unit of the hub housing, and is used to output power to the hub housing 61 when it engages with the pawl 15.

所述离心块19程弧形的块状结构，所述安装轴191被套设在所述弧形块状结构的尾部，离心块安装轴191直接设置在所述齿环13上，离心块19设置安装轴191上并且离心块19在离合结合时绕所述安装轴191转动，带动所述离合片17径向转动，在图4中所离心块和齿环13均逆时针转动。The centrifugal block has an arc-shaped block structure of 19 passes. The mounting shaft 191 is sleeved at the tail of the arc-shaped block structure. The centrifugal block installation shaft 191 is directly disposed on the ring gear 13 and the centrifugal block 19 is provided. The mounting shaft 191 and the centrifugal block 19 rotate around the mounting shaft 191 during the clutch coupling, which drives the clutch piece 17 to rotate radially, and the centrifugal block and the ring gear 13 are rotated counterclockwise in FIG. 4.

所述离心块19绕安装轴191转动是由于齿环13的转动使得离心块产生离心效应造成的，同时所述齿环13也作为离合装置的动力输入部，在离合结合时其与被驱动的花鼓壳体61同步转动，显然动力输入部还可以是非行星齿轮的其他转动部件，只要其能够转动使得离心块19形成有效的离心效应即可。The rotation of the centrifugal block 19 around the mounting shaft 191 is caused by the centrifugal effect of the centrifugal block caused by the rotation of the ring gear 13. At the same time, the ring gear 13 also serves as the power input part of the clutch device. The hub housing 61 rotates synchronously. Obviously, the power input part can also be other rotating parts other than the planetary gear, as long as it can rotate so that the centrifugal block 19 forms an effective centrifugal effect.

所述离心块19通过一驱动部192与所述离合片17连接；该驱动部192为设置在所述离心块安装轴191一侧与所述离合片17配接的驱动杆192，该驱动杆192一端套在所述离心块19的驱动杆安装孔内，驱动杆192的另外一端与所述离合片17上设置的配接的开口173抵触，所述驱动杆192部分的收容在所述开口173内。所述驱动部还可以是除轴以外的其他驱动形式例如使用钩、齿轮、棘轮、推杆、杠杆等机械结构代替所述驱动杆。The centrifugal block 19 is connected to the clutch plate 17 through a driving portion 192; the driving portion 192 is a driving rod 192 provided on the side of the centrifugal block mounting shaft 191 and mated with the clutch plate 17; the driving rod One end of 192 is sleeved in the driving rod mounting hole of the centrifugal block 19, the other end of the driving rod 192 is in contact with the matching opening 173 provided on the clutch plate 17, and the driving rod 192 is partially received in the opening. Within 173. The driving part may also be a driving form other than a shaft, for example, using a mechanical structure such as a hook, a gear, a ratchet, a push rod, or a lever instead of the driving rod.

在踏频逐渐上升到第一踏频时离心离合所述述离心块19转动因离心效应绕安装轴191转动，驱动轴192随着离心块19绕所述离心块安装轴191转动，驱动轴191通过所述离合片17上的收容槽170驱动离合片17径向转动。When the cadence gradually rises to the first cadence, the centrifugal clutch 19 rotates due to the centrifugal effect and rotates around the mounting shaft 191, and the drive shaft 192 rotates with the centrifugal block 19 around the centrifugal block installation shaft 191, and the drive shaft 191 The accommodating groove 170 on the clutch plate 17 drives the clutch plate 17 to rotate radially.

所述离合片17包括一棘爪收容槽170，其包括下边缘172和上边缘171，所述棘爪15被部分地收容在所述棘爪收容槽170；离合片17转动到所述棘爪能够脱离所述收容槽170的脱离位置，所述棘爪在弹簧的作用下从初始位置弹出，并与花鼓壳体的棘轮环标号162处啮合。在啮合位置所述棘爪15未被所述棘爪收容槽170收容的部分在离合结合时与所述花鼓壳体的驱动部16啮合。The clutch plate 17 includes a pawl receiving groove 170, which includes a lower edge 172 and an upper edge 171. The pawl 15 is partially received in the pawl receiving groove 170; the clutch plate 17 rotates to the pawl The pawl can be released from the disengaging position of the receiving groove 170, and the pawl is ejected from the initial position under the action of the spring, and is engaged with the ratchet ring number 162 of the hub shell. In the engaging position, the part of the pawl 15 not received by the pawl receiving groove 170 is engaged with the driving part 16 of the hub housing when the clutch is engaged.

所述棘爪包括一弧形支撑部153，所述弧形支撑部的背部设置有弹簧槽154，一轴向固定弹簧151穿过所述弹簧槽将其轴向固定在所述齿环14上；所述弹簧15压迫所述弧形支撑部的背部154使得棘爪15总是趋于远离所述棘爪收容槽170；因此一旦所述收容槽170转动到脱离位置时，所述棘爪15从收容槽170中脱出，并在弹簧的作用下以弧形支撑部为支点旋转一定角度后与驱动部192啮合。The pawl includes an arc-shaped support portion 153, a spring groove 154 is provided on the back of the arc-shaped support portion, and an axial fixing spring 151 passes through the spring groove to axially fix it on the ring gear 14 The spring 15 presses the back 154 of the arc-shaped support portion so that the pawl 15 always moves away from the pawl receiving groove 170; therefore, once the receiving groove 170 rotates to the disengaged position, the pawl 15 Released from the accommodation groove 170, and rotated by a certain angle with the arc-shaped support portion as a fulcrum under the action of the spring, and meshed with the driving portion 192.

在所述齿环13上包括棘爪安装位141，离合分离时棘爪的初始位置即被所述离合片上的收容槽170保持在此安装位中。在所述齿环13上关于中心对称的位置设置多个所述棘爪15。所述棘爪15安装位141为形成在所述齿环上的内凹结构，该内凹结构的体积略大于所述棘爪15的体积，所述离合片17转动棘爪与花鼓壳体61的驱动部啮合。The toothed ring 13 includes a pawl mounting position 141, and the initial position of the pawl is held in the mounting position by the receiving slot 170 on the clutch plate when the clutch is disengaged. A plurality of the pawls 15 are provided on the ring gear 13 at positions symmetrical to the center. The mounting position 141 of the pawl 15 is a concave structure formed on the ring gear. The volume of the concave structure is slightly larger than the volume of the pawl 15. The clutch plate 17 rotates the pawl and the hub shell 61. The driving part is engaged.

所述花鼓驱动部包括棘轮环16以及与棘轮环外齿啮合的固定齿环18。所述固定齿环18与花鼓壳体61固定连接或一体设置，或者将棘轮环与固定齿环简化为一个部件与花鼓壳体一体设置。所述棘轮环16的的内部包括多组棘齿，棘齿包括一棘爪收容部160和凸起部163，离合结合时，棘爪收容部160的前端为与所述棘爪的前端152抵触的配合槽162，啮合时所述棘爪通过该配合槽162将骑行动力传递到花鼓壳体上，所述凸起部163档住所述棘爪15使之不从配合槽中脱出。The hub driving part includes a ratchet ring 16 and a fixed toothed ring 18 that meshes with the outer teeth of the ratchet ring. The fixed toothed ring 18 is fixedly connected to or integrated with the hub shell 61, or the ratchet ring and the fixed toothed ring are simplified into a single component and integrally provided with the hub shell. The inside of the ratchet ring 16 includes a plurality of groups of ratchet teeth. The ratchet teeth include a pawl receiving portion 160 and a convex portion 163. When the clutch is coupled, the front end of the pawl receiving portion 160 is in contact with the front end 152 of the pawl. The engaging groove 162 transmits the riding force to the hub shell through the engaging groove 162 during engagement, and the protrusion 163 blocks the pawl 15 so as not to come out of the engaging groove.

在踏频从第二踏频逐渐上升到第一踏频时第一离心离合结合，所述花鼓壳体61的转速变为高档，其转速大于所述第二行星齿轮架21的转速；所述第二行星齿轮组2上的棘轮环26随花鼓壳体61同步转动使得第二离心离合棘轮环转速超过棘爪的转速，所述的分离部(相当于图5中标号163)转动超越并压迫所述棘爪使得棘爪回缩，进而迫使所述棘爪与棘轮环强制脱离。棘爪25与所述配合槽(相当于图5中标号162)脱离从而使得第二行星齿轮组进入空转状态。When the cadence gradually rises from the second cadence to the first cadence, the first centrifugal clutch is combined, and the rotation speed of the hub housing 61 becomes high-grade, and the rotation speed is greater than the rotation speed of the second planetary gear carrier 21; The ratchet ring 26 on the second planetary gear set 2 rotates synchronously with the hub housing 61 so that the rotation speed of the second centrifugal clutch ratchet ring exceeds the rotation speed of the pawl, and the separation part (equivalent to reference numeral 163 in FIG. 5) is turned over and pressed. The pawl retracts the pawl, thereby forcibly disengaging the pawl from the ratchet ring. The pawl 25 is disengaged from the engaging groove (corresponding to reference numeral 162 in FIG. 5), so that the second planetary gear set enters an idling state.

当所述踏频从高于第一踏频逐渐下降到第二踏频，此时由于惯性作用花鼓壳体61的转速大于所述第一齿环11的转速，所述棘轮环16超越棘爪15，并且位于棘爪15后方的凸起部163超越所述棘爪15，并将棘爪15推出所述收容槽160推回到所述安装位141，同时离心块19的复位力驱使离心块和离合片17反向复位转动，所述棘爪15再次进入离合片上的收容槽170中，此时由于收容槽170已经回到了初始位置因此所述棘爪被重新锁定回到安装位。而此时达到第二踏频，第二离心离合上的棘爪25与棘轮环26上的配合槽啮合，完成从高速档将为中速档的步骤。When the cadence gradually decreases from higher than the first cadence to the second cadence, the rotation speed of the hub shell 61 is greater than the rotation speed of the first ring gear 11 due to inertia, and the ratchet ring 16 surpasses the pawl. 15 and the protruding portion 163 located behind the pawl 15 surpasses the pawl 15 and pushes the pawl 15 out of the receiving slot 160 and pushes back to the installation position 141, and the resetting force of the centrifugal block 19 drives the centrifugal block The clutch plate 17 and the clutch plate 17 rotate in the opposite direction, and the pawl 15 enters the receiving groove 170 on the clutch plate again. At this time, the pawl is locked back to the installation position because the receiving groove 170 has returned to the initial position. At this time, the second cadence is reached, and the pawl 25 on the second centrifugal clutch is engaged with the matching groove on the ratchet ring 26 to complete the step from the high speed to the middle speed.

当用户突然停止踩踏，即踏频直接降为零所述第一行星齿轮组1的齿环11和第二行星齿轮组2的齿环21停止转动，从而使得所述第一行星齿轮上的棘爪15和第二行星齿轮的棘爪25，都从所述收容槽中脱出被突起部163推回到所述安装位141，同样地所述棘爪15重新被安装槽锁定，从而完成直接从高档降为低档。When the user suddenly stops stepping, that is, the cadence frequency is directly reduced to zero, the ring gear 11 of the first planetary gear set 1 and the ring gear 21 of the second planetary gear set 2 stop rotating, so that the ratchet on the first planetary gear set Both the pawl 15 and the pawl 25 of the second planetary gear are released from the receiving groove and pushed back to the mounting position 141 by the protruding portion 163. Similarly, the pawl 15 is locked again by the mounting groove to complete the direct removal from Downgrade from high to low.

所述离心块19与一复位件连接，离心块19始终受到复位力。所述复位件为设置在所述离心块安装轴上的扭簧，当然本领域技术人员还可以使用其他任意已知的复位手段代替所述扭簧。The centrifugal block 19 is connected to a resetting member, and the centrifugal block 19 is always subjected to a resetting force. The reset member is a torsion spring provided on the mounting shaft of the centrifugal block. Of course, those skilled in the art can also use any other known reset means to replace the torsion spring.

Claims

一种自动变速花鼓，其特征在于，包括：An automatic variable speed hub is characterized in that it includes:

花鼓壳体；Hub shell

作为支撑、安装结构的花鼓轴；Hub shaft as support and installation structure;

安装在所述花鼓轴上的至少两级行星齿轮组，不同所述行星齿轮组向花鼓壳体输出不同转速；At least two-stage planetary gear sets installed on the hub shaft, different planetary gear sets output different speeds to the hub housing;

相邻所述行星齿轮组的太阳轮或行星轮或齿环之间径向方向上不嵌套；There is no nesting in the radial direction between the sun gear or the planet gear or the ring gear of the adjacent planetary gear sets;

相邻所述行星齿轮组之间使用传动部连接。A transmission portion is connected between the adjacent planetary gear sets.
如权利要求1所述的一种自动变速花鼓，其特征在于，所述行星齿轮组包括：The automatic transmission hub according to claim 1, wherein the planetary gear set comprises:

第一行星齿轮组和第二行星齿轮组；A first planetary gear set and a second planetary gear set;

第一行星齿轮组的行星架与第二行星齿轮组的齿环通过所述传动部连接；The planet carrier of the first planetary gear set and the ring gear of the second planetary gear set are connected through the transmission part;

所述第一、第二行星齿轮组齿环或第二行星齿组的行星架用于驱动所述花鼓壳体；The ring gears of the first and second planetary gear sets or the planet carriers of the second planetary gear set are used to drive the hub shell;

离合组件，用于选择第一、第二行星齿轮组齿环或第二行星齿组的行星架驱动所述花鼓壳体。The clutch assembly is used for selecting the ring gear of the first or second planetary gear set or the planet carrier of the second planetary gear set to drive the hub housing.
如权利要求2所述的一种自动变速花鼓，其特征在于，所述离合组件包括：在第一踏频以上结合的第一离心离合；第二踏频以上结合的第二离心离合；The automatic variable speed hub according to claim 2, wherein the clutch component comprises: a first centrifugal clutch coupled above the first cadence; and a second centrifugal clutch coupled above the second cadence;

所述第二行星齿轮组，在踏频低于第二踏频时通过行星架驱动花鼓壳体；The second planetary gear set, when the cadence is lower than the second cadence, drives the hub shell through the planetary carrier;

所述第二行星齿轮组，在踏频高于第二踏频小于第一踏频时所述第二离心离合结合，并通过齿环驱动花鼓壳体；The second planetary gear set is combined with the second centrifugal clutch when the cadence is higher than the second cadence and less than the first cadence, and the hub shell is driven by the ring gear;

所述第一行星齿轮组，在踏频高于第一踏频时第一离心离合结合，并通过齿环驱动花鼓壳体。The first planetary gear set is coupled with the first centrifugal clutch when the cadence is higher than the first cadence, and drives the hub housing through the ring gear.
如权利要求3所述的一种自动变速花鼓，其特征在于，所述第一或第二离心离合包括：离心块、离合片、棘爪和棘轮环；The automatic variable speed hub according to claim 3, wherein the first or second centrifugal clutch comprises: a centrifugal block, a clutch piece, a pawl and a ratchet ring;

棘轮环，用于与所述棘爪啮合时向花鼓壳体输出动力；A ratchet ring for outputting power to the hub shell when engaging with the pawl;

离合结合时，离心块驱动离合片径向转动释放棘爪与棘轮环啮合；When the clutch is coupled, the centrifugal block drives the clutch to rotate radially to release the pawl to engage with the ratchet ring;

离合分离时，棘轮环的分离部转动迫使所述棘爪与棘轮环强制脱离。When the clutch is disengaged, the separation part of the ratchet ring is rotated to force the pawl to forcibly disengage from the ratchet ring.
如权利要求4所述的一种自动变速花鼓，其特征在于，所述棘轮环的分离部为径向向内延申的突起部，离合分离时所述分离部超越并压迫所述棘爪回缩。The automatic variable speed hub according to claim 4, characterized in that the separation part of the ratchet ring is a protrusion extending radially inwardly, and the separation part surpasses and presses the pawl back when the clutch is separated. Shrunk.
如权利要求5所述的一种自动变速花鼓，其特征在于，所述花鼓内设置用于与棘轮环外齿啮合的固定齿环，所述固定齿环与花鼓固定连接或一体设置，所述棘轮环的棘齿在离合结合时与所述及棘爪啮合。The automatic variable speed hub according to claim 5, wherein a fixed ring gear for meshing with the external teeth of the ratchet ring is provided in the hub, and the fixed ring ring is fixedly connected or integrally provided with the hub, The ratchet teeth of the ratchet ring mesh with the pawl when the clutch is engaged.
如权利要求5所述的一种自动变速花鼓，其特征在于，An automatic transmission hub according to claim 5, wherein:

所述离心块设置在所述齿环上的安装轴，离合结合时离心块绕所述安装轴转动时带动所述离合片径向转动；The centrifugal block is provided on a mounting shaft on the ring gear, and when the centrifugal block is rotated around the mounting shaft when the clutch is coupled, the clutch piece is driven to rotate radially;

所述离合片包括一棘爪收容槽，所述棘爪被部分地收容在所述棘爪收容槽；The clutch plate includes a pawl receiving groove, and the pawl is partially received in the pawl receiving groove;

离合片径向转动使得棘爪收容槽释放棘爪从初始位置转换到与所述花鼓壳体的驱动部啮合的位置。The clutch piece rotates radially so that the pawl receiving groove releases the pawl from the initial position to a position that engages with the driving part of the hub housing.
如权利要求3所述的一种自动变速花鼓，其特征在于，所述第二行星齿轮组的行星架通过棘爪与所述花鼓壳体啮合。The hub according to claim 3, wherein the planet carrier of the second planetary gear set is engaged with the hub shell by a pawl.
如权利要求1-7任一项所述的一种自动变速花鼓，其特征在于，所述传动部为套设在花鼓轴径向***的传动套筒，所述第二行星齿轮组和第一行星齿轮组的齿环设置与所述传动套筒连接的连接部。The hub according to any one of claims 1 to 7, wherein the transmission portion is a transmission sleeve sleeved on a radial periphery of the hub shaft, the second planetary gear set and the first The ring gear of the planetary gear set is provided with a connection portion connected with the transmission sleeve.
如权利要求1-7任一项所述的一种自动变速花鼓，其特征在于，所述第一行星齿轮组与第二行星齿轮组互为镜像设置。The hub according to any one of claims 1 to 7, wherein the first planetary gear set and the second planetary gear set are mirror images of each other.