CN106763570B - Single-wheel direct-drive multi-gear full-automatic transmission with fixed central wheel - Google Patents

Single-wheel direct-drive multi-gear full-automatic transmission with fixed central wheel Download PDF

Info

Publication number
CN106763570B
CN106763570B CN201611194299.4A CN201611194299A CN106763570B CN 106763570 B CN106763570 B CN 106763570B CN 201611194299 A CN201611194299 A CN 201611194299A CN 106763570 B CN106763570 B CN 106763570B
Authority
CN
China
Prior art keywords
pawl
piece
wheel
linkage
hub
Prior art date
Legal status (The legal status 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 status listed.)
Active
Application number
CN201611194299.4A
Other languages
Chinese (zh)
Other versions
CN106763570A (en
Inventor
黄英可
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Zhangjiagang Chuansuo Vehicle Industry Co Ltd
Original Assignee
Zhangjiagang Chuansuo Vehicle Industry Co Ltd
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 Zhangjiagang Chuansuo Vehicle Industry Co Ltd filed Critical Zhangjiagang Chuansuo Vehicle Industry Co Ltd
Priority to CN201611194299.4A priority Critical patent/CN106763570B/en
Publication of CN106763570A publication Critical patent/CN106763570A/en
Application granted granted Critical
Publication of CN106763570B publication Critical patent/CN106763570B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • 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
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • 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
    • 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
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital 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
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2038—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with three engaging means
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
    • Y02T10/86—Optimisation of rolling resistance, e.g. weight reduction 

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The invention discloses a single-wheel direct-drive multi-gear full-automatic transmission with a fixed central wheel, which comprises the following components: the center pin, wheel hub and speed change mechanism, speed change mechanism includes two at least sets of planetary gear trains and at least one set of automatic centrifugal gearshift, and every set of planetary gear train includes: in every two sets of planetary transmissions, the planetary carrier, the planetary gear ring and the central wheel form an assembly, the planetary carrier of the planetary transmission of the initial set is fixedly connected with the central shaft or integrally formed, each set of automatic centrifugal gear shifting mechanism comprises a pawl carrier, a ratchet wheel and at least one pawl, the pawl carrier is arranged in a hub, the ratchet wheel is arranged on the assembly or the gear ring, an overrunning clutch is arranged between the planetary carrier and the hub or the overrunning clutch is arranged between the assembly and the hub, and the transmission can reduce the requirement on pedal frequency in medium and high gears.

Description

Single-wheel direct-drive multi-gear full-automatic transmission with fixed central wheel
[ field of technology ]
The invention relates to the technical field of bicycles, in particular to a single-wheel direct-drive multi-gear full-automatic transmission with a fixed center wheel.
[ background Art ]
The bicycle speed variator is divided into an inner speed variator and an outer speed variator, the outer speed variator adopts an open type chain mechanism as a transmission system, and the chain is changed to different flywheels to realize different chain transmission ratios by stirring a gear shifter arranged in front of the bicycle. The internal transmission of the prior art has the following common defects: 1. manual gear shifting is needed, and automatic gear shifting cannot be realized; 2. when the internal transmission is shifted to the high gear, if the tread frequency is decreasing, it is difficult for the transmission to remain in the high gear.
[ invention ]
In order to solve the problems, the invention aims to provide a single-wheel fixed direct-drive multi-gear full-automatic transmission with a central wheel, which can reduce the requirement on pedal frequency.
In order to achieve the above purpose, the technical scheme adopted by the invention is as follows: a fixed single-wheel direct drive multi-speed full automatic transmission with a center wheel, comprising: the center pin, wheel hub and set up the speed change mechanism between center pin and wheel hub, the center pin is power input spare, wheel hub is power output spare, speed change mechanism includes two sets at least planetary gear and at least one set of automatic centrifugal gearshift, and every set of planetary gear includes: the automatic centrifugal gear shifting mechanism comprises a pawl carrier, a ratchet wheel and at least one pawl, wherein the pawl is arranged on the pawl carrier, the pawl carrier is arranged in a hub, the ratchet wheel is arranged on the assembly or the gear ring, an overrunning clutch is arranged between the planet carrier and the hub or between the assembly and the hub.
Preferably, a fixed single-wheel direct-drive multi-gear full automatic transmission in the present invention is further provided with: each set of automatic centrifugal gear shifting mechanism further comprises at least one linkage piece, the pawl piece is installed on the pawl fixing frame through a first connecting piece, the linkage piece is installed on the pawl fixing frame through a second connecting piece, the pawl piece and the linkage piece are arranged at intervals in the circumferential direction, and the pawl piece comprises: the first end, the second end and the first installation department that sets up between first end and second end are equipped with the pawl portion that cooperatees with the ratchet in the inner wall department of the second end of at least one pawl, the first installation department of pawl is equipped with the first mounting hole that is used for installing first connecting piece, the linkage includes third end, fourth end and sets up the second installation department between third end and fourth end, the second installation department of linkage is equipped with the second mounting hole that is used for installing the second connecting piece, the first end of pawl and/or the fourth end of linkage are equipped with the balancing weight, along radial direction the first end limit of pawl is located the inboard of the fourth end of linkage, the second end limit of pawl is located the inboard of the third end of linkage or along radial direction the fourth end limit of linkage is located the inboard of the second end of pawl, on the pawl or the linkage or on the linkage have the elastic component that is used for the initial position of pawl to install.
Preferably, a fixed single-wheel direct-drive multi-gear full automatic transmission in the present invention is further provided with: each automatic centrifugal gear shifting mechanism further comprises at least one linkage piece, the pawl pieces are mounted on the pawl fixing frame through first connecting pieces, one end of each linkage piece is movably connected with one of the adjacent pawl pieces, the other end of each linkage piece is movably connected with the other adjacent pawl pieces, each pawl piece and each linkage piece are arranged at intervals in the circumferential direction, each pawl piece comprises a first end portion, a second end portion and a first mounting portion arranged between the first end portion and the second end portion, a balancing weight is arranged at the first end portion of each pawl piece, pawl portions matched with the ratchet wheels are arranged at the inner wall of the second end portion of each pawl piece, first mounting holes for mounting the first connecting pieces are formed in the first mounting portions of the pawl pieces, and elastic pieces for controlling the initial positions of the pawl pieces are mounted on the pawl piece frame.
Preferably, a fixed single-wheel direct-drive multi-gear full automatic transmission in the present invention is further provided with: the pawl mount includes: the annular base and the plurality of mounting seats extend inwards from the inner wall of the annular base.
Preferably, a fixed single-wheel direct-drive multi-gear full automatic transmission in the present invention is further provided with: the elastic piece is a torsion spring, a spring or a spring piece.
Preferably, a fixed single-wheel direct-drive multi-gear full automatic transmission in the present invention is further provided with: the first connecting piece and the second connecting piece are pins.
Preferably, a fixed single-wheel direct-drive multi-gear full automatic transmission in the present invention is further provided with: the pawl piece and the linkage piece are arranged in an involute shape or an arc shape.
Preferably, a fixed single-wheel direct-drive multi-gear full automatic transmission in the present invention is further provided with: one end of the central shaft is provided with a boss, one end of the hub is provided with a first tightening piece, the other end of the hub is provided with a second tightening piece, the central shaft is connected with the first tightening piece through a bearing or a ball, the first tightening piece is connected with the hub through a bearing or a ball, and the second tightening piece is connected with the central wheel through a bearing or a ball
Compared with the prior art, the invention has the following beneficial effects: the single-wheel direct-drive multi-gear full-automatic transmission with the fixed central wheel has the advantages of compact structure, convenience in installation, high transmission efficiency, firm gear shifting and stable speed change, the full-automatic speed change can be realized by arranging a plurality of sets of automatic centrifugal gear shifting mechanisms in the transmission, the multi-gear speed change can be realized by increasing or decreasing the number of the automatic centrifugal gear shifting mechanisms and the planetary transmission in the gear shifting mechanisms, and in addition, the transmission can reduce the requirement on pedal frequency in middle and high gears, so that riding is easier.
[ description of the drawings ]
Fig. 1 is a schematic diagram of a front view of a fixed single-wheel direct-drive multi-speed full automatic transmission according to embodiment 1 of the present invention.
Fig. 2 is an exploded view of a fixed single-wheel direct-drive multi-speed full automatic transmission according to embodiment 1 of the present invention.
Fig. 3 is a schematic cross-sectional view taken along line A-A of fig. 1.
Fig. 4 is a schematic structural view of a first automatic centrifugal shift structure in embodiment 1 of the invention.
Fig. 5 is a schematic cross-sectional structure of a fixed single-wheel direct-drive multi-speed full automatic transmission in embodiment 2 of the present invention.
Fig. 6 is a schematic cross-sectional structure of a fixed single-wheel direct-drive multi-speed full automatic transmission in embodiment 3 of the present invention.
In the figure: 1. a central shaft, 10, a boss, 20, a first tightening member, 21, a second tightening member, 2, a hub, 3, a planetary transmission, 30, a first planetary transmission, 300, a first carrier, 301, a first planetary transmission, 302, a first ring gear, 303, a first sun gear, 31, a second planetary transmission, 310, a second carrier, 311, a second planetary transmission, 312, a second ring gear, 313, a second sun gear, 32, a third planetary transmission, 320, a third carrier, 321, a third planetary gear, 322, a third ring gear, 323, a third sun gear, 4, an automatic centrifugal shift mechanism, 40, a first automatic centrifugal shift mechanism, 400, a first pawl carrier, 4000, elastic member, 401, first pawl, 4010, first end, 4011, second end, 4012, first mounting portion, 4013, pawl portion, 402, first linkage, 4020, third end, 4021, fourth end, 4022, second mounting portion, 403, first ratchet, 41, second automatic centrifugal shift mechanism, 410, second pawl holder, 411, second pawl, 412, second linkage, 413, second ratchet, 42, third automatic centrifugal shift mechanism, 420, third pawl holder, 421, third pawl, 422, third linkage, 423, third ratchet, 5, overrunning clutch, 50, pawl, 51, ratchet.
[ detailed description ] of the invention
The following describes the single-wheel direct-drive multi-gear full-automatic transmission with a fixed center wheel in detail through specific embodiments.
Example 1
Referring to fig. 1 to 4, a center wheel fixed single wheel direct drive multi-speed full automatic transmission includes: the speed change mechanism comprises a central shaft 1, a hub 2 and a speed change mechanism arranged between the central shaft 1 and the hub 2, wherein the central shaft 1 is a power input part, the hub 2 is a power output part, and the speed change mechanism comprises at least two sets of planetary speed changers and at least one set of automatic centrifugal gear change mechanisms.
The planetary transmission 3 includes: a first planetary transmission 30, a second planetary transmission 31, and a third planetary transmission 32 disposed side by side, the first planetary transmission 30 including: the second planetary transmission 31 includes: the third planetary transmission 32 includes: the third planet carrier 320, the third planet wheel 321, the third gear ring 322 and the third sun wheel 323 are integrally formed to form an integral piece, the integral piece is sleeved on the central shaft 1 and is fixedly connected with the vehicle frame, in this embodiment, the first planet transmission is a starting sleeve planet transmission, namely, a planet transmission with power reaching first, the first planet carrier 300 of the starting sleeve planet transmission is connected with the central shaft 1 through a spline, the first gear ring 302 and the second planet carrier 310 are integrally formed to form a first assembly, the second gear ring 312 and the third planet carrier 320 are integrally formed to form a second assembly, an overrunning clutch 5 is arranged between the first planet carrier 300 and the wheel hub 2, the overrunning clutch 5 comprises a pawl 50 and a ratchet wheel 51, in this embodiment, the pawl 50 is arranged on the first planet carrier 300, the ratchet wheel 51 is arranged in the wheel hub 2, and in other embodiments, the pawl can be arranged in the wheel hub 2, and the ratchet wheel can be arranged on the first planet carrier 300.
The automatic centrifugal shift mechanism 4 includes: the first automatic centrifugal shift mechanism 40, the second automatic centrifugal shift mechanism 41 and the third automatic centrifugal shift mechanism 42, wherein the first automatic centrifugal shift mechanism 40 comprises a first pawl holder 400, three first pawls 401, three first links 402 and a first ratchet 403, and of course, in other embodiments, no links 402 or only one link 402 or only one pawl 401 is provided, the invention can be implemented as well. The first pawl cage 400 is disposed in the hub 2 and integrally formed with the hub 2, wherein the first ratchet wheel 403 is disposed on a first assembly of the first gear ring 302 and the second planet carrier 310, and an elastic member 4000 for controlling an initial position of the first pawl 401 is mounted on the first pawl cage 400, and the elastic member 4000 may be a torsion spring, a spring or a leaf spring, although in other embodiments, the elastic member 4000 may be mounted on the first pawl 401 or the first linkage member 402, which may also implement the present invention. The first pawls 401 and the first linking members 402 are each mounted on the first pawl cage 400 by pins, the three first pawls 401 and the three first linking members 402 are circumferentially spaced apart, and the first pawls 401 include: the first mounting portion 4012 is provided with a first mounting hole for mounting a pin, the first end portion 4010, the second end portion 4011 and a first mounting portion 4012 arranged between the first end portion 4010 and the second end portion 4011, in this embodiment, the inner wall of the second end portion 4011 of each first pawl 401 is provided with a pawl portion 4013 matched with the first ratchet 403, and in other embodiments, only the inner wall of the second end portion 4011 of one first pawl 401 is provided with a pawl portion 4013 matched with the first ratchet 403, or only the inner walls of the second end portions 4011 of two first pawls 401 are provided with pawl portions 4013 matched with the first ratchet 403, which can realize the invention. The first linkage 402 includes a third end 4020, a fourth end 4021, and a second mounting portion 4022 disposed between the third end 4020 and the fourth end 4021, the second mounting portion 4022 of the first linkage 402 is provided with a second mounting hole for mounting a pin, the first end 4010 of the first pawl 401 and the fourth end 4021 of the first linkage 402 are both provided with weights, the first end 4010 of the first pawl 401 is limited in the radial direction to the inner side of the fourth end 4021 of the first linkage 402, and the second end 4011 of the first pawl 401 is limited in the radial direction to the inner side of the third end 4020 of the first linkage 402. The first pawl 401 and the first link member 402 are arranged in an involute or arc configuration such that the angle of oscillation of the first pawl 401 is aligned with the angle of oscillation of the second pawl 411. The second automatic centrifugal shift mechanism 41 has the same structure as the first automatic centrifugal shift mechanism 40, and includes a second pawl holder 410, three second pawls 411, three second linkage members 412 and a second ratchet wheel 413, wherein the second pawl holder 410 is disposed in the hub 2 and is integrally formed with the hub 2, the second ratchet wheel 413 is disposed on a second assembly formed by the second gear ring 312 and the third planet carrier 320, the third automatic centrifugal shift mechanism 42 has the same structure as the first automatic centrifugal shift mechanism 40, and includes a third pawl holder 420, three third pawls 421, three third linkage members 422 and a third ratchet wheel 423, the third pawl holder 420 is disposed in the hub 2 and is integrally formed with the hub 2, and the third ratchet wheel 423 is disposed on the third gear ring 322. Of course, in other embodiments, the automatic centrifugal shifting mechanism may also have a structure that one end of the linkage member is movably connected with one of the adjacent pawls, and the other end of the linkage member is movably connected with the other adjacent pawl, that is, the linkage member may be respectively movably connected with two adjacent pawls by bending two ends, or the linkage member may be directly movably connected with two adjacent pawls by a pin, and at this time, the linkage member acts as a linkage corresponding to a balance pull rod, and the invention is similarly implemented.
The one end of center pin 1 is equipped with boss 10, the one end of wheel hub 2 is equipped with first tight piece 20, the other end of wheel hub 2 is equipped with second tight piece 21 that closes, pass through bearing or ball between center pin 1 and the first tight piece 20 and connect, pass through bearing or ball between first tight piece 20 and the wheel hub 2 and connect, pass through bearing or ball between second tight piece 21 and the center wheel and connect.
The working principle of the single-wheel direct-drive multi-gear full-automatic transmission with the fixed central wheel in the embodiment is as follows: when the first gear is at low speed, the pawl in the overrunning clutch is a normally open pawl, namely, the first planet carrier 300 and the hub 2 are always kept in an engaged state, power is input by the central shaft 1, because the central shaft 1 and the first planet carrier 300 are fixedly connected through the spline, power is transmitted to the first planet carrier 300, because the first planet carrier 300 is engaged with the hub 2, power is finally transmitted to the hub 2 and is output by the hub 2, along with the lifting of the rotating speed of the central shaft 1, the weight block end of the first pawl 401 of the first automatic centrifugal shifting mechanism 40 moves in a direction away from the axle center under the action of centrifugal force, because the weight block and the pawl of the first pawl 401 are respectively arranged at two ends of the first pawl 401, the pawl part end of the first pawl 401 moves towards the axle center direction based on the lever principle, thereby being engaged with the first ratchet 403 on the first assembly, when the first automatic centrifugal shift mechanism 40 works, the overrunning clutch is in a following state, power is input by the central shaft 1, the central shaft 1 is fixedly connected with the first planet carrier 300, so that the power is transmitted to the first planet carrier 300, the first planet carrier 300 transmits the power to the first gear ring 302 through the transmission of the first planet carrier 301, the first gear ring 302 and the second planet carrier 310 are integrally formed into a first assembly, the first assembly is meshed with the hub 2, so that the power is finally transmitted to the hub 2 and is output by the hub 2, the second gear medium speed is realized, when the rotating speed of the central shaft 1 is lifted again, the balancing weight end of the second pawl 411 of the second automatic centrifugal shift mechanism 41 moves in the direction away from the central shaft under the action of the centrifugal force, and the balancing weight and the pawl of the second pawl 411 are respectively arranged at two ends of the second pawl 411, based on the lever principle, the pawl end of the second pawl 411 moves toward the axial direction to engage with the second ratchet 413 on the second assembly, and when the second automatic centrifugal shift mechanism 41 is operated, the first automatic centrifugal shift mechanism and the overrunning clutch are in a following state, power is input from the central shaft 1, because the central shaft 1 is fixedly connected with the first carrier 300, power is transmitted to the first carrier 300, the first carrier 300 transmits power to the first ring gear 302 through the transmission of the first planet gears 301, power is transmitted to the second carrier 310 because the first ring gear 302 and the second carrier are integrally formed, power is transmitted to the second ring gear 312 through the transmission of the second planet gears 311, the second assembly is in turn engaged with the hub 2 because the second ring gear 312 and the third carrier 320 are integrally formed, therefore, the power is finally transmitted to the hub 2 and is output by the hub 2, the third speed is realized, when the rotational speed of the central shaft 1 is lifted again, the weight block end of the third pawl 421 of the third automatic centrifugal shift mechanism 42 moves in the direction away from the central shaft under the centrifugal force, because the weight block and the pawl of the third pawl 421 are respectively arranged at the two ends of the third pawl 421, based on the lever principle, the pawl part end of the third pawl 421 moves toward the axial direction, thereby being meshed with the third ratchet wheel 423 on the third gear ring 322, and the first automatic centrifugal shift mechanism, the second automatic centrifugal shift mechanism 41 and the overrunning clutch are all in the following state when the third automatic centrifugal shift mechanism 42 works, the power is input by the central shaft 1, because the central shaft 1 is fixedly connected with the first planet carrier 300, the power is transmitted to the first planet carrier 300, the first carrier 300 transmits power to the first ring gear 302 by the transmission of the first planetary gears 301, the second carrier 310 transmits power to the second carrier 310 by the integral formation of the first ring gear 302 and the second carrier 310, the second carrier 310 transmits power to the second ring gear 312 by the transmission of the second planetary gears 311, the third carrier 320 by the integral formation of the second ring gear 312 and the third carrier 320, and the third carrier 320 transmits power to the third ring gear 322 by the transmission of the third planetary gears 321, and the third ring gear 322 meshes with the hub 2, so that the power is finally transmitted to the hub 2 and is output by the hub 2. The single-wheel direct-drive multi-gear full-automatic transmission can reduce the requirement on pedal frequency in middle and high gears, for example: it is assumed that the operating speeds at which the first, second and third automatic centrifugal shift mechanism pawls are opened are 80 rpm, 120 rpm and 180 rpm, respectively. The speed ratio of the planetary speed change mechanism is 1.5, when the input speed of the central shaft is 70 revolutions per minute, the rotation speed of the hub is the same as the input speed of the central shaft, namely 70 revolutions per minute, and because the pawls of the first, second and third automatic centrifugal speed change mechanisms are arranged on the hub, the pawls of the first, second and third automatic centrifugal speed change mechanisms cannot be opened at the moment, and the power 1:1 is output by the hub, so that the first-gear low speed is realized. When the input rotation speed of the central shaft reaches 80 revolutions per minute, the rotation speed of the hub also reaches 80 revolutions per minute, and the pawl of the first automatic centrifugal shifting mechanism is opened and meshed with a ratchet wheel on a first assembly formed by integrally forming the first gear ring and the second planet carrier, so that a second gear intermediate speed is realized. At this time, the first gear ring and the second planet carrier are integrally formed to form a first assembly, and the rotation speed is 120 rpm (80 rpm, 1.5) which is far greater than the working rotation speed of 80 rpm when the pawl of the first automatic centrifugal mechanism is opened, so that the input rotation speed of the central shaft can be reduced, that is, the treading frequency can be reduced. When the input rotation speed of the central shaft is increased to 80 rpm again in the working state of opening the pawl of the first automatic centrifugal mechanism, the rotation speed of the hub is 120 rpm (80 rpm is 1.5), the pawl of the second automatic centrifugal shifting mechanism is opened and meshed with the ratchet wheel on the second assembly formed by integrally forming the second gear ring and the third planet carrier, so that a third gear medium speed is realized, and at the moment, the rotation speed of the first assembly formed by integrally forming the second gear ring and the third planet carrier is 180 rpm (120 rpm is 1.5) which is far greater than the operation rotation speed of opening the pawl of the second automatic centrifugal mechanism, so that the input rotation speed of the central shaft can be reduced, namely the trampling frequency can be reduced. In the operating state that the pawls of the first and second automatic centrifugal mechanisms are opened, when the input rotation speed of the central shaft is increased to 80 rpm again, the rotation speed of the hub is 180 rpm (120 rpm: 1.5), the pawls of the third automatic centrifugal shifting mechanism are opened and meshed with the ratchet of the third gear ring, and at the moment, the rotation speed of the third gear ring is 270 rpm (180 rpm: 1.5) which is far greater than the operating rotation speed of the pawls of the third automatic centrifugal mechanism, which is 180 rpm, so that the input rotation speed of the central shaft can be reduced, that is, the treading frequency can be reduced. The automatic centrifugal gear shifting is realized by a series of improvement of the input rotating speed, the trampling frequency is reduced, the input rotating speed is improved again, and the automatic centrifugal gear shifting cycle of the higher-level automatic centrifugal gear shifting is realized again.
In summary, the single-wheel direct-drive multi-gear full-automatic transmission has the advantages of compact structure, convenient installation, high transmission efficiency, firm gear shifting and stable speed change, the full-automatic speed change can be realized by arranging a plurality of sets of automatic centrifugal gear shifting mechanisms in the transmission, the multi-gear speed change can be realized by increasing or decreasing the number of the automatic centrifugal gear shifting mechanisms and the planetary transmission in the gear shifting mechanisms, and in addition, the transmission can reduce the requirement on pedal frequency in middle and high gears, so that riding is easier.
Example 2
Referring to fig. 5, the center wheel fixed single wheel direct drive multi-speed full automatic transmission in this embodiment is identical to the center wheel fixed single wheel direct drive multi-speed full automatic transmission in embodiment 1 in the rest of the structure, except that: in embodiment 1, three sets of automatic centrifugal shifting mechanisms are included in total, and an overrunning clutch is provided between the hub 2 and the first carrier 300, whereas in this embodiment, two sets of automatic centrifugal shifting mechanisms are included in total, the overrunning clutch is provided between the first assembly and the hub 2, i.e., compared to embodiment 1, embodiment 2 omits the first automatic centrifugal shifting mechanism 40, and places the overrunning clutch 5 originally provided between the first carrier 300 and the hub 2 at a position where the first automatic centrifugal shifting mechanism 40 is omitted.
The working principle of the single-wheel direct-drive multi-gear full-automatic transmission with the fixed central wheel in the embodiment is as follows: the pawl 50 in the overrunning clutch 5 is a normally open pawl, that is, the first assembly is always meshed with the hub 2, when the first gear is at a low speed, power is input by the central shaft 1, because the central shaft 1 is fixedly connected with the first planet carrier 300, the power is transmitted to the first planet carrier 300, the first planet carrier 300 transmits the power to the first gear ring 302 through the transmission of the first planet carrier 301, the first assembly is meshed with the hub 2 because the first gear ring 302 and the second planet carrier 310 are integrally formed into the first assembly, the power is transmitted to the hub 2 and is output by the hub 2, along with the lifting of the speed of the central shaft 1, the balancing weight end of the second pawl 411 of the second automatic centrifugal shifting mechanism 41 moves in the direction away from the axis under the action of centrifugal force, because the balancing weight and the pawl of the second pawl 411 are respectively arranged at two ends of the second pawl 411 based on the lever principle, the pawl end of the second pawl 411 moves toward the axial direction to engage with the second ratchet 413 on the second assembly, power is input from the center shaft 1, since the first carrier 300 is fixedly connected with the center shaft 1, power is transmitted to the first carrier 300, the first carrier 300 transmits power to the first ring gear 302 through the transmission of the first planet gears 301, power is transmitted to the second carrier 310 because the first ring gear 302 is integrally formed with the second carrier 310, power is transmitted to the second ring gear 312 through the transmission of the second planet gears 311, the second carrier 310 integrally forms the second assembly again to engage with the hub 2 because the second ring gear 312 is integrally formed with the third carrier 320, power is finally transmitted to the hub 2 and output from the hub 2, realizing a second speed intermediate speed when the speed of the center shaft 1 is again increased, the weight block end of the third pawl 421 of the third automatic centrifugal shift mechanism 42 moves in a direction away from the axle center under the action of centrifugal force, because the weight block and the pawl of the third pawl 421 are respectively disposed at both ends of the third pawl 421, the pawl end of the third pawl 421 moves in the direction of the axle center based on the lever principle, so as to mesh with the third ratchet 423 on the third ring gear 322, power is input from the central shaft 1, because the first carrier 300 is fixedly connected with the central shaft 1, power is transmitted to the first carrier 300, through the transmission of the first planet gears 301, the first carrier 300 transmits power to the first ring gear 302, because the first ring gear 302 and the second carrier 310 are integrally formed, power is transmitted to the second ring gear 312 through the transmission of the second planet gears 311, because the second ring gear 312 and the third carrier 320 are integrally formed, power is transmitted to the third carrier 320, through the transmission of the third planet gears 321, the third carrier 320 transmits power to the third ring gear 322, and finally, the speed is transmitted to the third hub 2 through the transmission of the third carrier 321, and the hub 2 is output.
Example 3
Referring to fig. 6, the center wheel fixed single wheel direct drive multi-speed full automatic transmission in this embodiment is identical to the center wheel fixed single wheel direct drive multi-speed full automatic transmission in embodiment 2 in the rest of the structure, except that: in embodiment 2, two sets of automatic centrifugal shift mechanisms and three sets of planetary transmissions are included in total, and in the present embodiment, one set of automatic centrifugal shift mechanism and two sets of planetary transmissions are included in total, i.e., the single-wheel direct-drive multi-speed full automatic transmission in the present embodiment eliminates the second planetary transmission 31 and the second automatic centrifugal shift mechanism 41 in embodiment 2, compared to embodiment 2.
The working principle of the single-wheel direct-drive multi-gear full-automatic transmission with the fixed central wheel in the embodiment is as follows: the pawl 50 in the overrunning clutch 5 is a normally open pawl, namely, the first assembly is always meshed with the hub 2, power is input by the central shaft 1 when the first gear is at a low speed, the central shaft 1 is fixedly connected with the first planet carrier 300, so that the power is transmitted to the first planet carrier 300, the first planet carrier 300 transmits the power to the first gear ring 302 through the transmission of the first planet carrier 301, the first assembly is meshed with the hub 2 again because the first gear ring 302 and the third planet carrier 320 are integrally formed into the first assembly, and the power is finally transmitted to the hub 2 and is output by the hub 2. With the rotation speed of the central shaft 1 being increased, the weight block end of the third pawl 421 of the third automatic centrifugal shift mechanism 42 moves in the direction away from the axis under the action of centrifugal force, because the weight block and the pawl of the third pawl 421 are respectively disposed at two ends of the third pawl 421, the pawl end of the third pawl 421 moves toward the axis based on the lever principle, so as to mesh with the third ratchet wheel 423 on the third gear ring 322, power is input by the central shaft 1, because the central shaft 1 is fixedly connected with the first planet carrier 300, the power is transmitted to the first planet carrier 300, the first planet carrier 300 transmits the power to the first gear ring 302 through the transmission of the first planet wheel 301, the power is transmitted to the third planet carrier 320 through the transmission of the third planet wheel 321, and the third planet carrier 320 transmits the power to the third gear ring 322, and because the third gear ring 322 meshes with the hub 2, the power is finally transmitted to the hub 2 and is output by the hub 2, so that the second high speed is realized.
The above-described embodiments are merely illustrative of the principles and functions of the present invention, and some of the practical examples, not intended to limit the invention; it should be noted that modifications and improvements can be made by those skilled in the art without departing from the inventive concept, and these are all within the scope of the present invention.

Claims (8)

1. The utility model provides a fixed single round of full-automatic derailleur of many grades of direct drive of center wheel which characterized in that includes: the center pin, wheel hub and set up the speed change mechanism between center pin and wheel hub, the center pin is power input spare, wheel hub is power output spare, speed change mechanism includes two sets at least planetary gear and at least one set of automatic centrifugal gearshift, and every set of planetary gear includes: the automatic centrifugal gear shifting mechanism comprises a pawl carrier, a ratchet wheel and at least one pawl, wherein the pawl is arranged on the pawl carrier, the pawl carrier is arranged in a hub, the ratchet wheel is arranged on the assembly or the gear ring, an overrunning clutch is arranged between the planet carrier and the hub or between the assembly and the hub.
2. The fixed single-wheel direct-drive multi-speed full automatic transmission of claim 1, wherein: each set of automatic centrifugal gear shifting mechanism further comprises at least one linkage piece, the pawl piece is installed on the pawl fixing frame through a first connecting piece, the linkage piece is installed on the pawl fixing frame through a second connecting piece, the pawl piece and the linkage piece are arranged at intervals in the circumferential direction, and the pawl piece comprises: the first end, the second end and the first installation department that sets up between first end and second end are equipped with the pawl portion that cooperatees with the ratchet in the inner wall department of the second end of at least one pawl, the first installation department of pawl is equipped with the first mounting hole that is used for installing first connecting piece, the linkage includes third end, fourth end and sets up the second installation department between third end and fourth end, the second installation department of linkage is equipped with the second mounting hole that is used for installing the second connecting piece, the first end of pawl and/or the fourth end of linkage are equipped with the balancing weight, along radial direction the first end limit of pawl is located the inboard of the fourth end of linkage, the second end limit of pawl is located the inboard of the third end of linkage or along radial direction the fourth end limit of linkage is located the inboard of the second end of pawl, on the pawl or the linkage or on the linkage have the elastic component that is used for the initial position of pawl to install.
3. The fixed single-wheel direct-drive multi-speed full automatic transmission of claim 1, wherein: each automatic centrifugal gear shifting mechanism further comprises at least one linkage piece, the pawl pieces are mounted on the pawl fixing frame through first connecting pieces, one end of each linkage piece is movably connected with one of the adjacent pawl pieces, the other end of each linkage piece is movably connected with the other adjacent pawl pieces, each pawl piece and each linkage piece are arranged at intervals in the circumferential direction, each pawl piece comprises a first end portion, a second end portion and a first mounting portion arranged between the first end portion and the second end portion, a balancing weight is arranged at the first end portion of each pawl piece, pawl portions matched with the ratchet wheels are arranged at the inner wall of the second end portion of each pawl piece, first mounting holes for mounting the first connecting pieces are formed in the first mounting portions of the pawl pieces, and elastic pieces for controlling the initial positions of the pawl pieces are mounted on the pawl piece frame.
4. A fixed single-wheel direct-drive multi-speed full automatic transmission according to claim 2 or 3, wherein: the pawl mount includes: the annular base and the plurality of mounting seats extend inwards from the inner wall of the annular base.
5. A fixed single-wheel direct-drive multi-speed full automatic transmission according to claim 2 or 3, wherein: the elastic piece is a torsion spring, a spring or a spring piece.
6. A fixed single-wheel direct-drive multi-speed full automatic transmission according to claim 2, wherein: the first connecting piece and the second connecting piece are pins.
7. A fixed single-wheel direct-drive multi-speed full automatic transmission according to claim 2, wherein: the pawl piece and the linkage piece are arranged in an involute shape or an arc shape.
8. The fixed single-wheel direct-drive multi-speed full automatic transmission of claim 1, wherein: the one end of center pin is equipped with the boss, wheel hub's one end is equipped with first tight piece that closes, wheel hub's the other end is equipped with the second and closes tight piece, pass through bearing or ball between center pin and the first tight piece that closes, pass through bearing or ball between first tight piece that closes and the wheel hub and connect, the second is closed tight piece and is connected through bearing or ball between the center wheel.
CN201611194299.4A 2016-12-21 2016-12-21 Single-wheel direct-drive multi-gear full-automatic transmission with fixed central wheel Active CN106763570B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201611194299.4A CN106763570B (en) 2016-12-21 2016-12-21 Single-wheel direct-drive multi-gear full-automatic transmission with fixed central wheel

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201611194299.4A CN106763570B (en) 2016-12-21 2016-12-21 Single-wheel direct-drive multi-gear full-automatic transmission with fixed central wheel

Publications (2)

Publication Number Publication Date
CN106763570A CN106763570A (en) 2017-05-31
CN106763570B true CN106763570B (en) 2023-07-14

Family

ID=58899103

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201611194299.4A Active CN106763570B (en) 2016-12-21 2016-12-21 Single-wheel direct-drive multi-gear full-automatic transmission with fixed central wheel

Country Status (1)

Country Link
CN (1) CN106763570B (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107061641B (en) * 2017-06-14 2023-09-08 张家港川梭车业有限公司 Double-wheel driving speed changer
CN107131263B (en) * 2017-06-14 2023-04-07 张家港川梭车业有限公司 Shaft input type three-gear inner speed changer
CN107339379B (en) * 2017-08-08 2023-06-16 张家港川梭车业有限公司 Movable three-gear speed change device of planetary transmission
CN108974243B (en) * 2018-09-12 2024-02-13 昆山唐泽新能源科技有限公司 Automatic speed-changing hub
US11565773B1 (en) * 2022-02-15 2023-01-31 New Kailung Gear Co., Ltd Gear switching control device of an internal derailleur

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3492893A (en) * 1967-08-11 1970-02-03 Shimano Industrial Co Three-stage speed change bicycle hub with built-in automatic speed change mechanism
US4594914A (en) * 1981-11-11 1986-06-17 Toyota Jidosha Kabushiki Kaisha Transverse type automatic transmission with intermediate power transfer through lay shaft
DE20320470U1 (en) * 2003-07-23 2004-09-16 Zf Friedrichshafen Ag Multi-stage automatic transmission with three planetary clusters, comprising single drive shaft acting with two clusters
CN1847083A (en) * 2006-05-11 2006-10-18 程辉 Automatic bicycle speed variator
CN102878259A (en) * 2012-09-28 2013-01-16 长城汽车股份有限公司 Multispeed automatic transmission and power assembly
CN104896040A (en) * 2015-05-14 2015-09-09 南宁学院 Multi-gear line control planetary gear automatic transmission
CN105402334A (en) * 2015-12-21 2016-03-16 江苏大学 Four-gear mechanical automatic transmission power assembly system based on planetary gear mechanisms
CN206398022U (en) * 2016-12-21 2017-08-11 张家港川梭车业有限公司 A kind of centre wheel fixes single-wheel and directly drives multi gear fully-automatic gearbox

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3492893A (en) * 1967-08-11 1970-02-03 Shimano Industrial Co Three-stage speed change bicycle hub with built-in automatic speed change mechanism
US4594914A (en) * 1981-11-11 1986-06-17 Toyota Jidosha Kabushiki Kaisha Transverse type automatic transmission with intermediate power transfer through lay shaft
DE20320470U1 (en) * 2003-07-23 2004-09-16 Zf Friedrichshafen Ag Multi-stage automatic transmission with three planetary clusters, comprising single drive shaft acting with two clusters
CN1847083A (en) * 2006-05-11 2006-10-18 程辉 Automatic bicycle speed variator
CN102878259A (en) * 2012-09-28 2013-01-16 长城汽车股份有限公司 Multispeed automatic transmission and power assembly
CN104896040A (en) * 2015-05-14 2015-09-09 南宁学院 Multi-gear line control planetary gear automatic transmission
CN105402334A (en) * 2015-12-21 2016-03-16 江苏大学 Four-gear mechanical automatic transmission power assembly system based on planetary gear mechanisms
CN206398022U (en) * 2016-12-21 2017-08-11 张家港川梭车业有限公司 A kind of centre wheel fixes single-wheel and directly drives multi gear fully-automatic gearbox

Also Published As

Publication number Publication date
CN106763570A (en) 2017-05-31

Similar Documents

Publication Publication Date Title
CN106763570B (en) Single-wheel direct-drive multi-gear full-automatic transmission with fixed central wheel
CN106494563B (en) Fixed single round of ring gear centre wheel directly drives multi-gear full-automatic derailleur
CN102470911B (en) Power transmission device for a chainless bicycle
CN106627975B (en) Single-wheel direct-drive transmission is trampled to straight line
JP4134183B2 (en) Bicycle transmission
CN101357669B (en) Hub transmission for a bicycle
CN206682233U (en) Single wheel drive two keeps off fully-automatic gearbox after a kind of
CN106741562B (en) Linear treading single-wheel direct-drive gear ring center wheel fixed transmission
CN106523608A (en) Third-gear dual-wheel-driven full automatic transmission
CN106481754B (en) A kind of multi gear automatic internal speed variator of real
CN106481755B (en) A kind of fixed Two-wheeled multi gear fully-automatic gearbox of centre wheel
CN106763569B (en) Gear ring double-center-wheel fixed single-wheel direct-drive multi-gear full-automatic transmission
CN107339379B (en) Movable three-gear speed change device of planetary transmission
CN106741561B (en) Three-gear full-automatic transmission
CN206511066U (en) A kind of gear ring center wheel fixes single-wheel and directly drives multi gear fully-automatic gearbox
CN107542863B (en) Three-planetary-row hybrid power two-gear automatic transmission assembly
CN106481756A (en) A kind of fixed Two-wheeled third gear fully-automatic gearbox of centre wheel gear ring
CN107588161B (en) Gear ring input double-wheel drive full-automatic multi-gear transmission
CN206361099U (en) A kind of fixed Two-wheeled third gear fully-automatic gearbox of centre wheel gear ring
CN206513771U (en) A kind of third gear Two-wheeled fully-automatic gearbox
CN206361097U (en) A kind of multi gear automatic internal speed variator of real
CN207378075U (en) A kind of gear ring inputs the full-automatic multi-shifting speed variator of Two-wheeled
CN206398022U (en) A kind of centre wheel fixes single-wheel and directly drives multi gear fully-automatic gearbox
CN206361100U (en) A kind of double centre wheels of gear ring fix single-wheel and directly drive multi gear fully-automatic gearbox
CN206394804U (en) A kind of third gear fully-automatic gearbox

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant