WO2015074444A1 - 自行车内变速器 - Google Patents

自行车内变速器 Download PDF

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Publication number
WO2015074444A1
WO2015074444A1 PCT/CN2014/084535 CN2014084535W WO2015074444A1 WO 2015074444 A1 WO2015074444 A1 WO 2015074444A1 CN 2014084535 W CN2014084535 W CN 2014084535W WO 2015074444 A1 WO2015074444 A1 WO 2015074444A1
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WO
WIPO (PCT)
Prior art keywords
wheel
ring
clutch
gear
control lever
Prior art date
Application number
PCT/CN2014/084535
Other languages
English (en)
French (fr)
Inventor
李激初
Original Assignee
李激初
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 李激初 filed Critical 李激初
Publication of WO2015074444A1 publication Critical patent/WO2015074444A1/zh

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M25/00—Actuators for gearing speed-change mechanisms specially adapted for cycles
    • B62M25/02—Actuators for gearing speed-change mechanisms specially adapted for cycles with mechanical transmitting systems, e.g. cables, levers
    • B62M25/04—Actuators for gearing speed-change mechanisms specially adapted for cycles with mechanical transmitting systems, e.g. cables, levers hand actuated
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M11/00—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels
    • B62M11/04—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio
    • B62M11/14—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears
    • B62M11/16—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears built in, or adjacent to, the ground-wheel hub

Definitions

  • the present invention relates to a bicycle internal transmission.
  • the bicycle transmission is divided into two categories: external transmission and internal transmission.
  • the external transmission adopts an open chain mechanism as the transmission system.
  • the structure is relatively simple. Different chain transmission ratios can be realized by dialing the chain to different toothed discs or flywheels, but outside.
  • the components of the transmission are exposed, easily interfered by external forces, resulting in unstable shifting action, and generally have the disadvantage of not long service life, and the noise during shifting is large;
  • the internal transmission is a planetary gear mechanism as the transmission main body, and the closed assembly
  • the above-mentioned drawbacks of the external transmission can be overcome, and the better transmission performance of the bicycle is provided, which is becoming more and more popular in bicycle production applications.
  • the gear position control mechanism of the internal transmission of the bicycle realizes different transmission ratios by controlling the engagement or separation of the sun gear or the carrier or the ring gear in the planetary gear mechanism, and the clutch mechanism applied to the internal transmission of the bicycle is usually a pawl Overrunning clutch, the traditional internal transmission separately controls the pawl action of the clutch between the gears of the planetary gear mechanism to realize the shifting. Therefore, in the process of controlling the shifting, multiple operating mechanisms need to be provided, and the operation is complicated, and at the same time, the transmission
  • the control actuator is implemented on the rear wheel axle of the bicycle.
  • the more gears of the internal transmission the more actuators are controlled, which makes the structure of the internal transmission complicated, and the handling is also very troublesome.
  • bicycle weight reduction is an important factor in bicycle speed competition.
  • the existing gear position control mechanism of the internal transmission obviously cannot adapt to the development of bicycles in this respect, which further restricts the promotion of the internal transmission on the bicycle.
  • the object of the present invention is to provide a bicycle internal transmission with simple structure and simple and convenient operation.
  • the shifting structure is simple, the shifting operation is convenient, the weight of the internal transmission can be effectively reduced, and the application of the internal transmission on the bicycle is further promoted.
  • the bicycle internal transmission includes a wheel axle 18, a planetary gear transmission mechanism and a gear position control mechanism.
  • the planetary gear transmission mechanism is disposed on the wheel axle, the input end of the planetary gear transmission mechanism is connected to the bicycle flywheel 6, and the output end is connected to the wheel hub 29,
  • the gear position control mechanism includes a steering assembly and a plurality of actuator assemblies; the steering assembly is disposed on the wheel axle 18 and includes an operating cam ring 4 that is sleeved over the wheel axle 18, the two ends of the steering cam ring Each is provided with an operating protrusion 3;
  • the actuator assembly is disposed inside the inner ring gear of the planetary gear transmission, and includes a central control lever 9 and a shaft control lever 10, the central control lever 9 and the shaft
  • the control lever 10 is movable in the axial direction of the wheel axle 18, wherein one end of the central control lever 9 is connected with the carrier of the planetary gear mechanism and the clutch mechanism of the ring gear, the shaft control One end of the rod 10 is coupled to a clutch mechanism
  • the steering assembly further includes a steering return torsion spring 2 that is coupled to the steering wheel ring 4 and is coupled to the wheel axle 18.
  • the steering assembly is disposed within the steering fixed housing 1 that is secured to one end of the wheel axle 18.
  • the shaft control lever 10 is embedded in a sliding groove provided on the surface of the wheel axle 18, and the shaft control lever 10 is provided with a control ratchet of the planetary gear transmission center wheel on the wheel axle 18. a claw-matching notch, the wheel axle 18 is respectively provided with a positioning shaft card 12 and a shaft control return spring 16, and the two ends of the shaft control lever 10 are respectively provided with the convex protrusions and the steering protrusions of the steering cam ring 4 It is in contact with the shaft control return spring 16.
  • the actuator assembly further includes a center wheel 11 that cooperates with the central control lever 9, and the center wheel 11 is sleeved on the wheel axle 18, and one end of the center wheel 11 is splined
  • the bicycle flywheel 6 is connected to the inner hole, and the other end is provided with a spline matching the inner spline groove of the inner transmission carrier 26, and the central control lever 9 is fixedly connected with a central control sleeve 32 which is fitted on the wheel axle 18 and passes through Controlling the middle sleeve 32 to contact the center wheel 11 achieves axial movement.
  • the clutch mechanism between the inner ring gear of the planetary gear transmission mechanism and the inner hole of the bicycle wheel hub is a pawl type overrunning clutch.
  • the center wheel 11 is disposed inside the ring gear, and an outer diameter of the center wheel 11 is in contact with a pawl portion located inside the ring gear.
  • the central control wheel 11 is connected with a matching synchronous control ring 22, and the synchronous control ring 22 and the central control wheel 11 are connected by a synchronous control rod 17, which synchronizes the outer diameter of the control ring 22 with the internal transmission.
  • the pawl portions inside the other inner ring gear are in contact.
  • the synchronous control lever 17 is inserted into the guide groove of the carrier 26, and is provided with a dial block that is in contact with the synchronous control ring 22.
  • the central control wheel 11, the synchronous control ring 22 and the synchronous control rod 17 are each provided with a return spring.
  • At least one end of the steering cam ring of the operating assembly is provided with inner and outer two-turn operating protrusions
  • the actuator assembly further includes at least one push rod 59, the push rod 59 being along the wheel axle
  • the axial movement of 18, one end of the push rod 59 is connected with a clutch mechanism provided between the flywheel 6 and the planetary gear transmission mechanism, and the other end of the push rod 59 is in contact with the operating protrusion provided at both ends of the operating cam ring 4,
  • a locating ring 35 is fixed to the wheel axle on one side of the steering cam ring 4, and the inner ring is provided with a groove corresponding to the cross section of the rod of the actuator for performing radial positioning of the assembly.
  • the planetary gear transmission mechanism includes a two-stage planetary gear transmission mechanism which is arranged side by side on the wheel axle, and the flywheel seat 36 of the flywheel 6 is connected to the first ring gear 43 via the ball type overrunning clutch 28, and A first clutch 37 is disposed between the flywheel seat 36 and the first planet carrier 42 as a power input connection clutch; the inner ring gears of the two-stage planetary gear transmission are connected by an internal ring gear overrunning clutch 46, wherein the second stage planet The ring gear and the carrier of the gear train are connected as outputs to the wheel hub through the overrunning clutch.
  • the push rod 59 is coupled to the first clutch 37 via a first push ring 39 that is fitted to the wheel axle, and the first clutch 37 is fitted over the first push ring 39 via the first clutch bearing 38.
  • the first push ring 39 is connected to the first clutch return spring 40.
  • the clutch mechanism connected to the central control lever 9 is a second clutch 49 that connects and disconnects the first ring gear 43 and the second carrier 51, and the outer ring of the second clutch 49 is disposed at the
  • the second inner ring gear pawl 52 which is openable on the inner wall of the two ring gear 53, is in contact with the second clutch 49, and the central control lever 9 is coupled to the second clutch 49 via a second push ring 48 that is fitted to the wheel axle.
  • the second clutch 49 is fitted to the second push ring 48 via the second clutch bearing 47, and the second push ring 48 is coupled to the second clutch return spring 50.
  • the invention controls a plurality of rod-shaped execution components through a steering component to realize the transformation of the transmission gear position, and the rod-shaped execution component can be embedded in the axial sliding groove on the wheel axle, thereby greatly simplifying the structure of the internal transmission, and
  • the size of the internal transmission is made smaller, effectively reducing the weight of the internal transmission, and the control assembly and the joystick assembly can be rotated without the wheel axle, reducing the wear and damage probability of the control assembly by setting the steering cam ring on the two
  • the convex contour of the end is matched with the movement of the actuator, and only the operation of one bicycle is required to realize the operation of the entire internal transmission, and the continuous shifting is realized by performing the cooperation between the components, and the gear position operation of the bicycle is simpler and more convenient.
  • the rod is arranged to accommodate the multi-stage planetary gear transmission of the high-end internal transmission.
  • the present invention can be applied to internal transmissions of different speeds, and the internal transmission can be further extended to bicycle applications.
  • Embodiment 1 is an exploded perspective view of a seven-speed internal transmission in Embodiment 1.
  • FIG. 2 is a schematic view showing the assembly of the seven-speed internal transmission in the first embodiment.
  • FIG 3 is a schematic structural view of the steering cam ring and the center control sleeve in the first embodiment.
  • FIG. 4 is a schematic view showing the control pawl of the shaft control lever and the center wheel in Embodiment 1.
  • Fig. 5 is a schematic view showing the deployment of the operating cam ring in the first embodiment.
  • FIG. 6 is a schematic diagram A of the transfer of the ten-speed internal transmission in the second embodiment.
  • Fig. 7 is a schematic diagram B of the transfer of the ten-speed internal transmission in the second embodiment.
  • Fig. 8 is an overall exploded perspective view of the ten-speed internal transmission in the second embodiment.
  • Figure 9 is a partially exploded perspective view A of the ten-speed internal transmission in the second embodiment.
  • Figure 10 is a partially exploded perspective view B of the ten-speed internal transmission in the second embodiment.
  • Figure 11 is a schematic exploded view of the steering cam ring in the second embodiment.
  • Figure 12 is a schematic view of the first clutch in the second embodiment.
  • Figure 13 is a schematic view of the first planet carrier in the second embodiment.
  • Figure 14 is a schematic view of the first ring gear in the second embodiment.
  • Figure 15 is a schematic view of the second clutch in the second embodiment.
  • Figure 16 is a schematic view of the second planet carrier in the second embodiment.
  • Figure 17 is a schematic view of the second ring gear in the second embodiment.
  • the shifting transmission mechanism is a double planetary gear transmission mechanism including an inner ring gear 7, a inner ring gear 20, and a carrier. 26, A center wheel 24 and B center wheel 25, the planet carrier 26 is provided with three double planetary gears 27 uniformly engaged with the A, B inner ring gear and the A and B center wheels.
  • the input end of the planetary gear transmission is connected to the flywheel 6 of the wheel (the bicycle rear wheel sprocket), the output end is connected to the wheel hub 29, the first bearing 5 is disposed between the flywheel 6 and the wheel axle 18, and the flywheel 6 and the wheel hub 29 are disposed.
  • a ball-type overrunning clutch 28 is also disposed between the inner holes, and the inner ring gear 7 and the inner ring gear 20 are provided with elastic pawls that can be opened and retracted, and the spline grooves provided in the inner holes of the wheel hub 29 constitute a ratchet type.
  • Two pawls are arranged on the wheel axle 18, and the spline grooves provided in the inner holes of the center wheels of the A and B respectively constitute a pawl type overrunning clutch device.
  • the pawls in the internal transmission are assembled by the pawl springs 13, and a bevel is provided on the side of the pawl, which can be conveniently closed or opened by the control mechanism.
  • the internal transmission of the present invention further includes a gear position control mechanism including a steering assembly and a plurality of actuator assemblies; the steering assembly is disposed at one end of the bicycle wheel axle 18 and includes an operating cam ring 4 that is sleeved over the wheel axle 18, Both ends of the steering cam ring are provided with steering projections 3.
  • a gear position control mechanism including a steering assembly and a plurality of actuator assemblies; the steering assembly is disposed at one end of the bicycle wheel axle 18 and includes an operating cam ring 4 that is sleeved over the wheel axle 18, Both ends of the steering cam ring are provided with steering projections 3.
  • the actuator assembly is disposed inside the inner ring gear of the transmission, including a central control lever 9 and a shaft control lever 10, and the central control lever 9 and the shaft control lever 10 are all along the wheel axle.
  • the central control lever 9 is connected to the inner transmission carrier and the clutch mechanism of the two inner ring gears and controls the opening and closing thereof, and the axis control lever 10
  • the clutch mechanism of the inner center wheel of the inner transmission is connected and controlled to open and close; the central control lever 9 and the shaft control lever 10 are respectively in contact with the operating protrusions at both ends of the steering cam ring 4; the steering cam ring 4 is connected to the pull wire 33 for rotation.
  • the axis control lever 10 is embedded in an axial chute provided on the surface of the wheel axle 18, and the shaft control lever 10 is provided with a notch of the controllable pawl 14 that cooperates with the A center wheel 24 on the wheel axle 18.
  • the notch of the moving axis control lever 10 is aligned with the controllable pawl 14 to open the stowable controllable pawl 14.
  • the corresponding pawl of the B center wheel 25 is the normally open pawl 15, and the axis control lever 10 does not Take control.
  • a positioning shaft card 12 and a shaft control return spring 16 are respectively disposed on the wheel axle 18, and the two ends of the shaft control lever 10 are respectively provided with the protrusions and the steering protrusions of the steering cam ring 4 and the shaft control return spring 16 respectively.
  • the positioning shaft card 12 positions the shaft control lever 10 in the chute, and the shaft control return spring 16 is used for returning the shaft control lever 10.
  • the actuator assembly further includes a center wheel 11 that cooperates with the central control lever 9, and the center wheel 11 is sleeved on the wheel axle 18, and one end of the center wheel 11 passes through the spline and the inner hole of the bicycle flywheel 6.
  • the other end is provided with a spline matching the inner spline groove of the inner transmission carrier 26, and the central control wheel 11 can slide back and forth between the bicycle flywheel 6 and the carrier 26, and the central control lever 9 is fixedly connected to a set.
  • the central control sleeve 32 on the wheel axle 18 controls the central control sleeve 32 to contact the central control wheel 11 to achieve axial movement.
  • the central control wheel 11 is disposed inside the inner ring gear 7 of the A, and the outer ring of the central control wheel 11 is in contact with a portion of the inner ring gear pawl 8 inside the inner ring gear, and normally the A inner ring gear pawl 8 is retracted; At the same time, the central control wheel 11 is connected with a matching synchronous control ring 22, and the synchronous control ring 22 and the central control wheel 11 are connected by a synchronous control rod 17, and the synchronous control ring 22 is disposed in the B inner ring gear 20, and the outer ring In contact with the inside of the B inner ring pawl 21, the B inner ring gear 21 is normally stowed.
  • the synchronizing lever 17 is inserted into the guide groove of the carrier 26, and is provided with a dial which is in contact with the synchronizing control ring 22.
  • the central control wheel 11, the synchronous control ring 22 and the synchronous control rod 17 are each provided with a return spring for performing the return of the assembly, wherein the central control wheel spring 30 is fitted on the wheel axle 18, and the synchronous control coil spring 23 is set on the planet.
  • the synchronous lever spring 19 can be disposed in the guide groove of the carrier with one end of the synchronous control lever 17.
  • the steering assembly also includes a steering return torsion spring 2 that is coupled to the steering wheel ring 4 and that is coupled to the steering wheel ring 4.
  • the steering assembly is disposed within the steering housing 1 and the steering housing 1 is secured to one end of the wheel axle 18.
  • the flywheel 6 transmits the input power to the A ring gear 7 through the ball type overrunning clutch 28 disposed thereon, and the A ring gear 7 transmits power to the carrier 26 through the planetary gear 27 meshed therewith.
  • the B center wheel 25 is fixedly driven by the normally open pawl 15, the controllable pawl 14 of the A center wheel 24 is closed by the axis control lever 10, the A center wheel 24 is idling, and the planet carrier 26 is meshed by the planet wheel 27 and the B center wheel 25.
  • the axis control lever 10 has been returned, the B center wheel 25 is fixedly driven by the normally open pawl 15, the controllable pawl 14 of the A center wheel 24 is closed by the axis control lever 10, and the A center wheel 24 is idling, the planet carrier 26 is rotated by the planetary wheel 27 and the B center wheel 25, at which time the rotational speed of the wheel hub 29 has exceeded the carrier 26, the ball-type overrunning clutch between the carrier 26 and the wheel hub 29 is disengaged, and the carrier 26 passes the planetary gear 27.
  • the A center wheel 24 is fixedly driven by the controllable pawl 14, and the rotation of the A inner ring gear Accelerating, the B center wheel 25 is driven by the planetary gear 27 to move beyond the normally open pawl 15 to achieve idling.
  • the planet carrier 26 meshes with the A center wheel 24 through the planetary gear 27 to transmit power to the A ring gear 7, A ring gear 7 and wheel hub
  • the pawl-type overrunning clutch between 29 outputs power to the wheel hub 29, which is the fifth gear.
  • the rotation speed of the wheel hub 29 has exceeded the A ring gear 7, so the A inner ring pawl 8 fails, which is the sixth gear position; similarly, in this state, the central control The lever 9 remains inactive, and the controllable lever 10 is pushed to open the controllable pawl 14 again by manipulating the cam ring 4, in this case A
  • the wheel 24 is fixedly driven by the controllable pawl 14, the speed of the A ring gear is increased, the B center wheel 25 is driven by the planet gear 27 to move beyond the normally open pawl 15, and the planet carrier 26 meshes with the A center wheel 24 via the planet gear 27.
  • the pawl type overrunning clutch between the B inner ring gear 20 and the wheel hub 29 transmits power to the wheel hub 29, which is the seventh gear position.
  • the ten-speed internal transmission is ten shifting positions
  • the shifting mechanism includes a two-stage planetary gear transmission mechanism
  • the first-stage planetary gear transmission mechanism is connected with the flywheel as an input terminal, and second.
  • the second ring gear of the planetary gear train and the second carrier are coupled to the hub as an output, wherein the first stage planetary gear has only one first center wheel 41, and the three sets of first planet wheels 44 meshing therewith pass
  • the first planetary gear shaft 45 is disposed on the first planet carrier 42
  • the second stage planetary gear transmission mechanism includes a second center wheel 56 and a third center wheel 57, and the pair of the second center wheel 56 and the third center wheel 57 mesh
  • the second planetary gear 55 is disposed on the second planet carrier 51 via the second planetary gear shaft 54.
  • the assembly of the hub is the same as that of the first embodiment, and the flywheel seat 36 of the flywheel 6 is coupled to the first ring gear 43 via the ball overrunning clutch 28.
  • An inner ring gear overrunning clutch 46 is disposed between the first inner ring gear 43 and the second inner ring gear 53.
  • the second inner ring gear 53 is provided with an openable second ring gear pawl 52 and an inner wall of the wheel hub 29 Splined slot connection, second planet carrier 51
  • a second carrier overrunning clutch 58 is disposed on the outer ring to connect to the inner wall of the wheel hub 29 .
  • the execution component of the gear position control mechanism of the embodiment includes a central control lever 9, a shaft control lever 10, and a push rod 59.
  • the central control lever 9, the axis control lever 10, and the push rod 59 can all be along the vehicle.
  • the clutch mechanism between the center wheels is connected, one end of the push rod 59 is connected with the clutch mechanism between the flywheel seat 36 and the planetary gear transmission mechanism; the other end of the central control lever 9 and the other end of the shaft control lever 10 are respectively associated with the steering cam
  • the operating projections at both ends of the ring 4 are in contact, and the other end of the push rod 59 is in contact with the inner ring operating projection at the same end of the central control lever 9.
  • the steering cam ring 4 is disposed in the steering fixed casing 1, and the steering fixed casing 1 is fixed to one end of the wheel axle 18, and is provided with a wire guiding sleeve 34 for guiding the wire in the tangential direction of the operating cam ring 4.
  • the steering cam ring 4 in this embodiment is as shown in FIG. 11, and one end of the planetary gear mechanism is provided with inner and outer two-circle steering protrusions 3 for controlling the central control.
  • the rod 9 and the push rod 59 are provided with a ring of operating projections at the other end for controlling the shaft control lever 10.
  • a set locating ring 35 is secured to the side of the actuating cam ring 4 adjacent the planetary gearing mechanism and is provided with a corresponding recess in the actuator assembly for manipulating the radial positioning of the assembly.
  • the inner and outer two-turn operating projections can be further disposed on both ends of the operating cam ring, and four rod-shaped actuators can be controlled at the same time.
  • the clutch mechanism to which the axis control lever 10 of the present embodiment is coupled is a controllable pawl 14 that controls the connection and separation between the wheel axle 18 and the planet gears of the second stage planetary gear train.
  • the clutch mechanism connected by the push rod 59 through the first push ring 39 is a first clutch 37 that controls the flywheel mount 36 to be coupled and disconnected from the first planet carrier 42, the first clutch 37 passing through the first clutch bearing. 38 is placed on the first push ring 39, and the first push ring 39 is connected to the first clutch return spring 40.
  • one end of the first clutch 37 is engaged with the inner hole of the flywheel seat 36 by a sliding spline, and the other end is provided with a clutch connecting tooth to be connected with the inner hole of the first carrier 42 of FIG.
  • the clutch mechanism connected to the central control lever 9 is a second clutch 49 that controls the connection and separation of the first ring gear 43 and the second carrier 51.
  • the outer ring of the second clutch 49 and the inner wall of the second ring gear 53 are located.
  • the openable second ring gear pawl 52 is in contact, the second ring gear pawl 52 is retracted, and the second clutch 49 is connected to the central control lever 9 via a second push ring 48 that is sleeved on the wheel axle.
  • a second clutch bearing 47 is disposed between the second clutch 49 and the second push ring 48, and a second clutch return spring 50 is coupled to the second push ring 48.
  • the second clutch 49 is provided with a spline connected to the inner hole of the first ring gear 43 in FIG. 14 at one end, and a clutch connecting tooth connected to the second carrier 51 of FIG. 16 at the other end. .
  • the internal transmission of the present embodiment is superimposed by the planetary gear transmission mechanisms of the front and rear stages to obtain the speed ratio of the ten gear positions, wherein the first stage planetary gear transmission mechanism has two speed ratio changes through the first clutch control 37, The secondary planetary gear transmission mechanism is controlled by the second clutch 49 and the controllable pawl 14 to control the change of the five speed ratios.
  • the specific change process of the ten gear positions of the present embodiment will be described below with reference to FIGS. 6 to 17:
  • the power transmission route of the first gear is: flywheel seat 36---ball type overrunning clutch 28---first inner ring gear 43---inner ring gear overrunning clutch 46---second inner ring gear 53-- -
  • the second planet gear 55 and the third center wheel 57 mesh - the second planet carrier 51 - the second planet carrier overrunning clutch 58 - the wheel hub 29 .
  • the steering cam drive shaft control lever 10 opens the controllable pawl 14 between the second center wheel 56 and the wheel axle, and at this time, the speed ratio of the double gear of the second center wheel 56 and the second planet gear 55 Increasing, the rotation speed of the third center wheel 57 exceeds the rotation speed of the wheel axle, and the speed ratio of the second gear position is generated at this time, and the power transmission route is: flywheel seat 36---ball type overrunning clutch 28---first inner Ring gear 43---ring gear overrunning clutch 46---second ring gear 53---the second planet gear 55 meshes with the second center wheel 56---the second planet carrier 51---the second planet Overrunning clutch 58---wheel hub 29.
  • the input end of the second stage planetary gear transmission mechanism is a second inner ring gear, and the output end is a second carrier 51.
  • the control cam ring drives the central control lever 9 to further advance, and the second clutch 49 further directly connects the first ring gear 43 with the second carrier 51, and at this time, the second carrier 51 and the first ring gear Synchronizing as the input end of the second stage planetary gear transmission mechanism, the rotation speed of the second inner ring gear 53 exceeds the first inner ring gear as the output end of the second stage planetary gear transmission mechanism at the speed increase of the planetary gear transmission mechanism.
  • the axis control lever 10 retracts the controllable pawl 14 between the second center wheel 56 and the wheel axle, and the third center wheel 57 meshes with the second planet gear 55 to form a speed ratio of the fourth gear: its power transmission
  • the route is as follows: flywheel seat 36---ball overrunning clutch 28---first inner ring gear 43---second planet carrier 51 --- The second planetary gear 55 and the third center wheel 57 are engaged - the second ring gear 53 - the second ring gear pawl 52 - the wheel hub 29 .
  • the steering cam ring drives the shaft control lever 10 to advance the controllable pawl 14 between the second center wheel 56 and the wheel axle again, and the double gear of the second center wheel 56 and the second planet gear 55 at this time.
  • the speed ratio is increased, and the rotation speed of the third center wheel 57 is driven to exceed the rotation speed of the wheel axle.
  • the speed ratio of the fifth gear position is generated, and the power transmission route is as follows: the flywheel seat 36---the ball type overrunning clutch 28- -- First inner ring gear 43 --- second planet carrier 51 --- The second planet gear 55 and the second center wheel 56 mesh - the second ring gear 53 - the second ring gear pawl 52 - the wheel hub 29 .
  • the first center wheel 41 and the first planet gear 44 of the first stage planetary gear transmission idle, and do not participate in the power transmission.
  • the steering cam ring drives the axis control lever 10 and the central control lever 9 to return to the position of the first gear position, and simultaneously drives the first push ring 39 to move forward and be connected thereto.
  • the first clutch 37 connects the flywheel seat 36 with the first planet carrier 42.
  • the first planet carrier 42 participates in power transmission as an input end of the first stage planetary gear transmission mechanism, and the rotation speed of the first inner ring gear 43 at this time
  • the control cam ring maintains the position of the first clutch, and the axis control lever 10 and the central control lever 9 are repeatedly controlled.
  • the above three stages a, b, and c are realized, and the changes of the sixth to tenth positions are realized.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

一种自行车内变速器，设有档位控制机构，包括一个操纵组件和若干个杆状执行组件（9，10）；操纵组件包括一个空套在车轮轴（18）上的操纵凸轮环（4），操纵凸轮环（4）的两端均设有操纵凸起（3）；通过一个操纵组件控制多个杆状执行组件（9，10）进而控制内变速器内部的各个离合器动作；杆状执行组件（9，10）嵌装在车轮轴（18）上，使得变速器的结构精简、重量减轻；操纵凸起（3）的轮廓与杆状执行组件（9，10）的动作进行匹配，只需一个自行车指拨即可实现内变速器的操作，档位操作简单方便；同时内变速器可适用于不同速别的内变速器，实用性提高。

Description

自行车内变速器
技术领域
本发明涉及一种自行车内变速器。
背景技术
自行车变速器分为外变速器和内变速器两大类，外变速器是采用开放式链条机构为传动系统，结构较为简单，通过拨动链条到不同的齿盘或飞轮上实现不同的链条传动比，但是外变速器的构件外露，容易受到外力的干扰，产生换挡动作不稳定，并且普遍具有使用寿命不长的缺点，换挡过程中噪音较大；内变速器是以行星齿轮机构作为传动主体，同时封闭装配在自行车的后车轮轴的花鼓内，能够克服外变速器存在的上述缺陷，提供自行车较佳的传动性能，其在自行车的生产应用中越来越普及。
自行车的内变速器的档位控制机构是通过控制行星齿轮机构中的中心齿轮或行星架或内齿圈的咬合或分开实现不同的传动速比，应用在自行车内变速器上的离合机构通常是棘爪式超越离合器，传统的内变速器单独地控制行星齿轮机构的齿轮之间离合器的棘爪动作实现变速，因此在控制变档过程中，需要设置多个操纵机构实现，操作复杂，同时，这种变速器的控制执行机构是套装在自行车后车轮轴上实现，一般内变速器的档位越多，控制的执行机构也越多，造成内变速器的结构复杂，同时操纵起来也十分麻烦。另一方面，自行车轻量化是自行车在速度竞赛中的重要因素，内变速器的现有档位控制机构明显不能适应自行车在这方面的发展，进一步制约了内变速器在自行车上的推广。
发明内容
本发明的目的是提供一种结构简单、操纵简单方便的自行车内变速器，换挡结构简单，换挡操作方便，可以有效的减轻内变速器的重量，有利于进一步推广内变速器在自行车上的应用。
本发明采用如下技术方案实现： 自行车内变速器，包括车轮轴18、行星齿轮传动机构和档位控制机构，所述行星齿轮传动机构设置在车轮轴上，行星齿轮传动机构的输入端连接自行车飞轮6，输出端连接车轮花鼓29，所述档位控制机构包括一个操纵组件以及若干个执行组件；所述操纵组件设置在车轮轴18上，包括一个空套在车轮轴18上的操纵凸轮环4，所述操纵凸轮环的两端均设有操纵凸起3；所述执行组件设置在所述行星齿轮传动机构的内齿圈内部，包括一个中控控制杆9和一个轴控控制杆10，所述中控控制杆9和轴控控制杆10均可沿车轮轴18的轴向移动，其中，所述中控控制杆9的一端与所述行星齿轮传动机构的行星架以及内齿圈的离合机构连接，所述轴控控制杆10的一端与所述车轮轴18与行星齿轮传动机构的中心轮之间的离合机构连接；所述中控控制杆9的另一端以及轴控控制杆10的另一端分别与操纵凸轮环4两端的操纵凸起接触；所述操纵凸轮环4与拉线33连接实现转动。
进一步的，所述操纵组件还包括套装在车轮轴18上与操纵凸轮环4连接的操纵回位扭簧2。
所述操纵组件设置在操纵固定外壳1内，所述操纵固定外壳1固设在车轮轴18一端。
在本发明中，所述轴控控制杆10嵌装在所述车轮轴18表面设置的滑槽内，轴控控制杆10上设有与车轮轴18上的行星齿轮传动机构中心轮的控制棘爪匹配的缺口，所述车轮轴18上分别套装有定位轴杆卡12和轴控回位弹簧16，轴控控制杆10的两端设置凸块分别与所述操纵凸轮环4的操纵凸起和轴控回位弹簧16接触。
在本发明中，所述执行组件还包括一个与中控控制杆9配合的中控轮11，所述中控轮11空套在车轮轴18上，所述中控轮11一端通过花键与自行车飞轮6内孔连接，另一端设有与内变速器行星架26内孔花键槽匹配的花键，所述中控控制杆9固定连接一个套装在车轮轴18上的中控套32，并通过控制所述中控套32与中控轮11接触实现轴线移动。
具体的，所述行星齿轮传动机构的内齿圈与自行车车轮花鼓内孔之间的离合机构为棘爪式超越离合器。
作为本发明的优选方案，所述中控轮11设置在所述内齿圈内部，中控轮11的外径与位于所述内齿圈内部的棘爪部分接触。
更进一步，所述中控轮11连接有一个配套的同步控制圈22，所述同步控制圈22与中控轮11之间通过同步控制杆17连接，同步控制圈22的外径与内变速器中其他内齿圈内部的棘爪部分接触。
其中，所述同步控制杆17插装在行星架26的导向槽内，其上设有与同步控制圈22接触的拨块。
所述中控轮11、同步控制圈22以及同步控制杆17均设有回位弹簧。
在本发明的进一步方案中，所述操纵组件的操纵凸轮环至少其中一端设有内外两圈操纵凸起，所述执行组件还包括至少一根推杆59，所述推杆59可沿车轮轴18的轴向移动，所述推杆59一端与设置在飞轮6和行星齿轮传动机构之间的离合机构连接，推杆59的另一端与操纵凸轮环4两端设置的操纵凸起接触，所述操纵凸轮环4一侧的车轮轴上固设有定位圈35，其内圈设有与执行组件的杆件截面对应的凹槽用于执行组件的径向定位。
进一步的，所述行星齿轮传动机构包括并排套装在车轮轴上的两级行星齿轮传动机构，所述飞轮6的飞轮座36通过滚珠式超越离合器28与第一内齿圈43连接，并且，所述飞轮座36与第一行星架42之间设有第一离合器37作为动力输入连接离合器；两级行星齿轮传动机构的内齿圈之间通过内齿圈超越离合器46连接，其中第二级行星齿轮传动机构的内齿圈和行星架作为输出端与车轮花鼓通过超越式离合器连接。
进一步的，所述推杆59通过套装在车轮轴上的第一推环39与第一离合器37连接，所述第一离合器37通过第一离合器轴承38套装在第一推环39上，所述第一推环39连接有第一离合器回位弹簧40。
进一步的，所述中控控制杆9连接的离合机构为实现第一内齿圈43和第二行星架51连接和分离的第二离合器49，所述第二离合器49的外圈与设置在第二内齿圈53内壁上可打开的第二内齿圈棘爪52接触，并且，所述中控控制杆9通过套装在车轮轴上的第二推环48与第二离合器49连接，所述第二离合器49通过第二离合器轴承47套装在第二推环48上，所述第二推环48连接有第二离合器回位弹簧50。
本发明通过一个操纵组件控制多个杆状执行组件，实现变速器档位的变换，杆状执行组件可嵌装在车轮轴上的轴向滑槽内，极大精简了内变速器的结构，可将内变速器的尺寸做得更小，有效减轻了内变速器的重量，并且，控制组件和操纵杆组件可不用随车轮轴一同转动，减少了控制组件的磨损和损坏几率，通过设置操纵凸轮环上两端的凸起轮廓与执行组件的运动匹配，只需要一个自行车的指拨即可实现整个内变速器的操作，通过执行组件之间的配合实现连续换挡，自行车的档位操作更简单方便，通过增加推杆的设置，可适应高档位的内变速器的多级行星齿轮传动机构。
由上所述，本发明能够适用不同速别的内变速器上，可以进一步将内变速器推广到自行车应用中。
以下结合附图和具体实施方式对本发明做进一步说明。
附图说明
图1为实施例1中的七速内变速器的分解示意图。
图2为实施例1中的七速内变速器的装配示意图。
图3为实施例1中的操纵凸轮环以及中控套的结构示意图。
图4为实施例1中的轴控控制杆与中心轮的控制棘爪示意图。
图5为实施例1中的操纵凸轮环展开示意图。
图6为实施例2中的十速内变速器的转配示意图A。
图7为实施例2中的十速内变速器的转配示意图B。
图8为实施例2中的十速内变速器的整体分解示意图。
图9为实施例2中的十速内变速器的局部分解示意图A。
图10为实施例2中的十速内变速器的局部分解示意图B。
图11为实施例2中的操纵凸轮环展开示意图。
图12为实施例2中的第一离合器示意图。
图13为实施例2中的第一行星架示意图。
图14为实施例2中的第一内齿圈示意图。
图15为实施例2中的第二离合器示意图。
图16为实施例2中的第二行星架示意图。
图17为实施例2中的第二内齿圈示意图。
图中标号：1-操纵固定外壳，2-操纵回位扭簧，3-操纵凸起，4-操纵凸轮环，5-第一轴承，6-飞轮，7-A内齿圈，8-A内齿圈棘爪，9-中控控制杆，10-轴控控制杆，11-中控轮，12-定位轴杆卡，13-棘爪弹簧，14-可控棘爪，15-常开棘爪，16-轴控回位弹簧，17-同步控制杆，18-车轮轴，19-同步控制杆弹簧，20-B内齿圈，21-B内齿圈棘爪，22-同步控制圈，23-同步控制圈弹簧，24-A中心轮，25-B中心轮，26-行星架，27-行星轮，28-滚珠式超越离合器，29-车轮花鼓，30-中控轮弹簧，31-第二轴承，32-中控套，33-拉线；34-拉线定向套，35-定位圈，36-飞轮座，37-第一离合器， 38-第一离合器轴承，39-第一推环，40-第一离合器回位弹簧，41-第一中心轮，42-第一行星架，43-第一内齿圈，44-第一行星轮，45-第一行星轮轴，46-内齿圈超越离合器，47-第二离合器轴承，48-第二推环，49-第二离合器，50-第二离合器回位弹簧，51-第二行星架，52-第二内齿圈棘爪，53-第二内齿圈，54-第二行星轮轴，55-第二行星轮，56-第二中心轮，57-第三中心轮，58-第二行星架超越离合器，59-推杆。
具体实施方式
实施例1
参见图1和图2，图示中为七个档位的七速内变速器，其变速传动机构为一个双联行星齿轮传动机构，包括有A内齿圈7、B内齿圈20、行星架26，A中心轮24以及B中心轮25，行星架26上设有均布设有三个双联行星轮27分别与A、B内齿圈和A、B中心轮啮合。行星齿轮传动机构的输入端连接车轮的飞轮6（自行车后轮链轮），输出端连接车轮花鼓29，飞轮6与车轮轴18之间设置第一轴承5，飞轮6与车轮花鼓29之间设置第二轴承31，其中第一轴承与第二轴承均采用推力轴承，飞轮6一端的外圈与A内齿圈7的内孔之间通过滚珠式超越离合器28装配，行星架26与车轮花鼓29的内孔之间同样设有滚珠式超越离合器28，A内齿圈7以及B内齿圈20上设有可打开收回的弹性棘爪，与车轮花鼓29内孔设置的花键槽组成棘爪式超越离合装置。在车轮轴18上设有两个棘爪，分别与A、B中心轮内孔设置的花键槽组成棘爪式超越离合装置。内变速器中的棘爪均采用棘爪弹簧13装配，并在棘爪的侧面上设置斜面，可在控制机构的作用下方便关闭或开启。
本发明的内变速器还包括有档位控制机构，其包括有一个操纵组件以及若干个执行组件；操纵组件设置在自行车车轮轴18一端，包括一个空套在车轮轴18上的操纵凸轮环4，操纵凸轮环的两端设有操纵凸起3。
结合参见图3和图4，执行组件设置在内变速器内齿圈内部，包括一个中控控制杆9和一个轴控控制杆10，中控控制杆9和轴控控制杆10均可沿车轮轴18的轴向移动。其中，中控控制杆9连接内变速器行星架以及两个内齿圈的离合机构并控制其开启和关闭，轴控控制杆10 连接内变速器中心轮的离合机构并控制其开启和关闭；中控控制杆9和轴控控制杆10分别与操纵凸轮环4两端的操纵凸起接触；操纵凸轮环4与拉线33连接实现转动。
具体的，轴控控制杆10嵌装在车轮轴18表面设置的轴向滑槽内，轴控控制杆10上设有与车轮轴18上的A中心轮24配合的可控棘爪14的缺口，移动轴控控制杆10的缺口与可控棘爪14对齐可将收起的可控棘爪14打开，B中心轮25对应的棘爪为常开棘爪15，轴控控制杆10不对其进行控制。在车轮轴18上分别套装有定位轴杆卡12和轴控回位弹簧16，轴控控制杆10的两端设置凸块分别与操纵凸轮环4的操纵凸起和轴控回位弹簧16接触，定位轴杆卡12将轴控控制杆10定位在滑槽内，轴控回位弹簧16用于轴控控制杆10的回位。
具体参见图1，在执行组件还包括一个与中控控制杆9配合的中控轮11，中控轮11空套在车轮轴18上，中控轮11一端通过花键与自行车飞轮6内孔连接，另一端设有与内变速器行星架26内孔花键槽匹配的花键，中控轮11可在自行车飞轮6与行星架26之间来回滑移，中控控制杆9固定连接一个套装在车轮轴18上的中控套32，控制中控套32与中控轮11接触实现轴线移动。
中控轮11设置在A内齿圈7内部，中控轮11的外圈与A内齿圈棘爪8在内齿圈内部的部分接触，常态下将A内齿圈棘爪8收起；同时，中控轮11连接有一个配套的同步控制圈22，同步控制圈22与中控轮11之间通过同步控制杆17连接，同步控制圈22设置在B内齿圈20内，其外圈与B内齿圈棘爪21内部的部分接触，常态下将B内齿圈21收起。同步控制杆17插装在行星架26的导向槽内，其上设有与同步控制圈22接触的拨块。
中控轮11、同步控制圈22以及同步控制杆17均设有回位弹簧用于执行组件的回位，其中，中控轮弹簧30套装在车轮轴18上，同步控制圈弹簧23套装在行星架26上，同步控制杆弹簧19可随同步控制杆17一端设置在行星架的导向槽内。
操纵组件还包括套装在车轮轴18上与操纵凸轮环4连接的操纵回位扭簧2。操纵组件设置在操纵固定外壳1内，操纵固定外壳1固设在车轮轴18一端。
结合参见图5中操纵凸轮环的展开示意图，操作本实施例中的变速器进行变速的步骤如下：
a 、常态下，飞轮6通过其上设置的滚珠式超越离合器28将输入的动力传递至A内齿圈7，A内齿圈7通过与其啮合的行星轮27将动力传递至行星架26，此时B中心轮25由常开棘爪15固定传动，A中心轮24的可控棘爪14被轴控控制杆10关闭，A中心轮24空转，行星架26由行星轮27与B中心轮25啮合转动，通过行星架26上设置的滚珠式超越离合器将动力输出至车轮花鼓29，此为一个档位；在此状态下，中控控制杆9不动作，通过操纵凸轮环4推动轴控控制杆10打开可控棘爪14，此时A中心轮24由可控棘爪14固定传动，A内齿圈的转速加快，B中心轮25被行星轮27带动超越常开棘爪15实现空转，行星架26由行星轮27与A中心轮24啮合转动，通过行星架26上设置的滚珠式超越离合器将动力输出至车轮花鼓29，此为第二个档位。
b 、继续转动操纵凸轮环4，推动中心控制杆9，进一步推动中控轮11，中控轮11滑移将A内齿圈8上的A内齿圈棘爪8打开，动力从飞轮6传输至A内齿圈8后，直接通过A内齿圈与车轮花鼓29之间的棘爪式超越离合装置将动力输出至车轮花鼓29，行星架以及B内齿圈皆空转，此为第三个档位。
c 、在b的基础上，继续转动操纵凸轮环4，推动中心控制杆9，将中控轮6的外花键与行星架26的内花键咬合，动力从飞轮6直接传输至行星架26，此时轴控控制杆10已回位，B中心轮25由常开棘爪15固定传动，A中心轮24的可控棘爪14被轴控控制杆10关闭，A中心轮24空转，行星架26由行星轮27与B中心轮25啮合转动，此时车轮花鼓29的转速已超越行星架26，行星架26与车轮花鼓29之间的滚珠式超越离合器分离失效，行星架26通过行星轮27与B中心轮25啮合传递动力至A内齿圈7，A内齿圈7与车轮花鼓29之间的棘爪式超越离合装置将动力输出至车轮花鼓29，B内齿圈由于B内齿圈棘爪21被同步控制圈关闭而空转，此为第四个档位；同理，在此状态下，中控控制杆9保持不动作，通过操纵凸轮环4推动轴控控制杆10再次打开可控棘爪14，此时A中心轮24由可控棘爪14固定传动，A内齿圈的转速加快，B中心轮25被行星轮27带动超越常开棘爪15实现空转，行星架26通过行星轮27与A中心轮24啮合传递动力至A内齿圈7，A内齿圈7与车轮花鼓29之间的棘爪式超越离合装置将动力输出至车轮花鼓29，此为第五个档位。
d 、在c的基础上，继续转动操纵凸轮环4，推动中心控制杆9，中控轮11通过同步控制杆17推动同步控制圈22，同步控制圈22移位，将B内齿圈20上的B内齿圈棘爪21打开，动力从飞轮6直接传输至行星架26后，此时轴控控制杆10已回位，B中心轮25由常开棘爪15固定传动，A中心轮24的可控棘爪14被轴控控制杆10关闭，A中心轮24空转，行星架26由行星轮27与B中心轮25啮合转动，车轮花鼓29的转速提高，与行星架26与之间的滚珠式超越离合器分离失效，行星架26通过行星轮27与B中心轮25啮合传递动力至B内齿圈20，B内齿圈20与车轮花鼓29之间的B内齿圈棘爪21将动力输出至车轮花鼓29，此时，车轮花鼓29的转速已超越A内齿圈7，因此A内齿圈棘爪8失效，此为第六个档位；同理，在此状态下，中控控制杆9保持不动作，通过操纵凸轮环4推动轴控控制杆10再次打开可控棘爪14，此时A中心轮24由可控棘爪14固定传动，A内齿圈的转速加快，B中心轮25被行星轮27带动超越常开棘爪15实现空转，行星架26通过行星轮27与A中心轮24啮合传递动力至B内齿圈20，B内齿圈20与车轮花鼓29之间的棘爪式超越离合装置将动力输出至车轮花鼓29，此为第七个档位。
实施例2
参见图6至图10，图示中的为十个变速档位的十速内变速器，其变速机构包括两级行星齿轮传动机构，第一级行星齿轮传动机构与飞轮连接作为输入端，第二级行星齿轮传动机构的第二内齿圈和第二行星架与花鼓连接作为输出端，其中第一级行星齿轮传动机构只有一个第一中心轮41，与其啮合的三组第一行星轮44通过第一行星轮轴45设置在第一行星架42上，第二级行星轮齿轮传动机构包括第二中心轮56和第三中心轮57，与第二中心轮56和第三中心轮57啮合的双联第二行星轮55通过第二行星轮轴54设置在第二行星架51上，花鼓的装配与实施例1相同，飞轮6的飞轮座36通过滚珠式超越离合器28与第一内齿圈43连接，第一内齿圈43与第二内齿圈53之间设有内齿圈超越离合器46，第二内齿圈53上设有可打开的第二内齿圈棘爪52与车轮花鼓29内壁的花键槽连接，第二行星架51的外圈上设有第二行星架超越离合器58与车轮花鼓29内壁连接。
具体的，本实施例的档位控制机构的执行组件包括中控控制杆9、轴控控制杆10和推杆59，中控控制杆9、轴控控制杆10和推杆59均可沿车轮轴18的轴向移动，其中，中控控制杆9的一端与行星齿轮传动机构的行星架以及内齿圈的离合机构连接，轴控控制杆10的一端与车轮轴18与行星齿轮传动机构的中心轮之间的离合机构连接，推杆59一端与飞轮座36和行星齿轮传动机构之间的离合机构连接；中控控制杆9的另一端以及轴控控制杆10的另一端分别与操纵凸轮环4两端的操纵凸起接触，推杆59的另一端与中控控制杆9同一端的内圈操纵凸起接触。操纵凸轮环4设置在操纵固定外壳1内，操纵固定外壳1固设在车轮轴18一端，其上设有将拉线沿操作凸轮环4切线方向引入的拉线定向套34。
由于本实施例中有三个执行组件，因此，本例中的操纵凸轮环4如附图11所示，靠近行星齿轮机构的一端设有内外两圈操纵凸起3，分别用于控制中控控制杆9和推杆59，另一端设有一圈操纵凸起，用于控制轴控控制杆10。在操纵凸轮环4靠近行星齿轮传动机构的一侧固定套装定位圈35，其上设有与执行组件中对应的凹槽，用于操纵组件的径向定位。
在其他的超过十速的内变速器上，可更近一步在操纵凸轮环的两端均设置内外两圈操纵凸起，同时控制四根杆状执行元件，此方案应为本领域技术人员可预见的，因此不再此另作赘述。
具体参见图7，本实施例中的轴控控制杆10连接的离合机构为控制车轮轴18与第二级行星齿轮传动机构的行星轮之间连接和分离的可控棘爪14。
结合参见图12至图17，推杆59通过第一推环39连接的离合机构为控制飞轮座36与第一行星架42连接和分离的第一离合器37，第一离合器37通过第一离合器轴承38套装在第一推环39上，第一推环39连接有第一离合器回位弹簧40。如图12所示，第一离合器37一端与飞轮座36的内孔通过滑移花键配合，另一端设有离合连接齿与图13中的第一行星架42内孔连接。
中控控制杆9连接的离合机构为控制第一内齿圈43和第二行星架51实现连接和分离的第二离合器49，第二离合器49的外圈与位于第二内齿圈53内壁的可打开的第二内齿圈棘爪52接触，将第二内齿圈棘爪52收起，第二离合器49通过套装在车轮轴上的第二推环48与中控控制杆9连接，第二离合器49与第二推环48之间设有第二离合器轴承47，第二推环48连接有第二离合器回位弹簧50。如图15所示，第二离合器49一端设有与图14中的第一内齿圈43内孔连接的花键，另一端设有与图16中的第二行星架51连接的离合连接齿。
本实施例的内变速器通过前后两级的行星齿轮传动机构进行叠加，取得十个档位的速比，其中第一级行星齿轮传动机构通过第一离合器控制37具有两个速比的变化，第二级行星齿轮传动机构通过第二离合器49和可控棘爪14配合控制具有五个速比的变化，以下结合图6至图17说明操作本实施例的十个档位的具体变化过程：
a 、首先一档的动力传递路线是：飞轮座36---滚珠式超越离合器28---第一内齿圈43---内齿圈超越离合器46---第二内齿圈53---第二行星轮55和第三中心轮57啮合---第二行星架51---第二行星架超越离合器58---车轮花鼓29。
然后，转动操纵凸轮驱动轴控控制杆10将第二中心轮56与车轮轴之间的可控棘爪14打开，此时第二中心轮56与第二行星轮55的双联齿轮的速比增大，第三中心轮57的转速超越车轮轴的转速，此时产生第二档位的速比，其动力传递路线为：飞轮座36---滚珠式超越离合器28---第一内齿圈43---内齿圈超越离合器46---第二内齿圈53---第二行星轮55和第二中心轮56啮合---第二行星架51---第二行星架超越离合器58---车轮花鼓29。
上述两档位中，第二级行星齿轮传动机构的输入端为第二内齿圈，输出端为第二行星架51。
b 、控制操纵凸轮环驱动中控控制杆9向前推进，与之连接的第二离合器49前移，将其压制的第二内齿圈53上的第二内齿圈棘爪52打开，实现第二内齿圈53与车轮花鼓内壁直接连接，此时的速比又较第二档增大，达到第三档位的速比，其动力传递的路线为：飞轮座36---滚珠式超越离合器28---第一内齿圈43---内齿圈超越离合器46---第二内齿圈53---第二内齿圈棘爪52---车轮花鼓29。
c 、控制操纵凸轮环驱动中控控制杆9进一步向前推进，第二离合器49进一步将第一内齿圈43与第二行星架51直接连接，此时第二行星架51与第一内齿圈同步作为第二级行星齿轮传动机构的输入端，第二内齿圈53的转速在行星齿轮传动机构的增速下超过第一内齿圈作为第二级行星齿轮传动机构的输出端，此时，轴控控制杆10收回第二中心轮56与车轮轴之间的可控棘爪14，由第三中心轮57与第二行星轮55啮合，形成第四档位的速比：其动力传递路线如下：飞轮座36---滚珠式超越离合器28---第一内齿圈43---第二行星架51 ---第二行星轮55和第三中心轮57啮合---第二内齿圈53---第二内齿圈棘爪52---车轮花鼓29。
然后，转动操纵凸轮环驱动轴控控制杆10再次推进将第二中心轮56与车轮轴之间的可控棘爪14打开，此时第二中心轮56与第二行星轮55的双联齿轮的速比增大，第三中心轮57的转速被带动超越车轮轴的转速，此时产生第五档位的速比，其动力传递路线如下：飞轮座36---滚珠式超越离合器28---第一内齿圈43---第二行星架51 ---第二行星轮55和第二中心轮56啮合---第二内齿圈53---第二内齿圈棘爪52---车轮花鼓29。
上述五个档位中，第一级行星齿轮传动机构中的第一中心轮41和第一行星轮44空转，均不参与动力传动。
d 、在完成上述五个档位后，此时转动操纵凸轮环驱动轴控控制杆10和中控控制杆9回到第一档位的位置，同时驱动第一推环39前移，与之连接的第一离合器37将飞轮座36与第一行星架42连接，此时，第一行星架42作为第一级行星齿轮传动机构的输入端参与动力传递，此时第一内齿圈43的转速经行星齿轮传动后超越飞轮座36的转速成为第一级行星齿轮传动机构的输出端，此时操纵凸轮环保持第一离合器的位置的同时，重复控制轴控控制杆10和中控控制杆9实现上述a、b、c三个阶段，实现第六至第十档位的变化。
上述仅为本实用新型在七速和十速内变速器上的实施例，但所属领域的技术人员应该明白，本实用新型所涉及的内变速器应该不限定于上述的变速器，在不脱离所附权利要求书所限定的本实用新型的精神和范围内，在其他速别的内变速器上对本实用新型所作出的各种应用，都属于本实用新型的保护范围。

Claims (14)

1 、自行车内变速器，包括车轮轴（18）、行星齿轮传动机构和档位控制机构，所述行星齿轮传动机构设置在车轮轴上，行星齿轮传动机构的输入端连接自行车飞轮（6），输出端连接车轮花鼓（29），其特征在于：
所述档位控制机构包括一个操纵组件以及若干个执行组件；
所述操纵组件设置在车轮轴（18）上，包括一个空套在车轮轴（18）上的操纵凸轮环（4），所述操纵凸轮环的两端均设有操纵凸起（3）；
所述执行组件设置在所述行星齿轮传动机构的内齿圈内部，包括一个中控控制杆（9）和一个轴控控制杆（10），所述中控控制杆（9）和轴控控制杆（10）均可沿车轮轴（18）的轴向移动，其中，所述中控控制杆（9）的一端与所述行星齿轮传动机构的行星架以及内齿圈的离合机构连接，所述轴控控制杆（10）的一端与所述车轮轴（18）与行星齿轮传动机构的中心轮之间的离合机构连接；所述中控控制杆（9）的另一端以及轴控控制杆（10）的另一端分别与操纵凸轮环（4）两端的操纵凸起接触；
所述操纵凸轮环（4）与拉线（33）连接实现转动。
2 、根据权利要求1所述的自行车内变速器，其特征在于：所述操纵组件还包括套装在车轮轴（18）上与操纵凸轮环（4）连接的操纵回位扭簧（2）。
3 、根据权利要求2所述的自行车内变速器，其特征在于：所述操纵组件设置在操纵固定外壳（1）内，所述操纵固定外壳（1）固设在车轮轴（18）一端。
4 、根据权利要求1所述的自行车内变速器，其特征在于：所述轴控控制杆（10）嵌装在所述车轮轴（18）表面设置的滑槽内，轴控控制杆（10）上设有与车轮轴（18）上的行星齿轮传动机构中心轮的控制棘爪匹配的缺口，所述车轮轴（18）上分别套装有定位轴杆卡（12）和 轴控回位弹簧（16） ，轴控控制杆（10）的两端设置凸块分别与所述操纵凸轮环（4）的操纵凸起和轴控回位弹簧（16）接触。
5 、根据权利要求1所述的自行车内变速器，其特征在于：所述执行组件还包括一个与中控控制杆（9）配合的中控轮（11），所述中控轮（11）空套在车轮轴（18）上，所述中控轮（11）一端通过花键与自行车飞轮（6）内孔连接，另一端设有与内变速器行星架（26）内孔花键槽匹配的花键，所述中控控制杆（9）固定连接一个套装在车轮轴（18）上的中控套（32），并通过控制所述中控套（32）与中控轮（11）接触实现轴线移动。
6 、根据权利要求5所述的自行车内变速器，其特征在于：所述行星齿轮传动机构的内齿圈与自行车车轮花鼓内孔之间的离合机构为棘爪式超越离合器。
7 、根据权利要求6所述的自行车内变速器，其特征在于：所述中控轮（11）设置在所述内齿圈内部，中控轮（11）的外径与位于所述内齿圈内部的棘爪部分接触。
8 、根据权利要求7所述的自行车内变速器，其特征在于：所述中控轮（11）连接有一个配套的同步控制圈（22），所述同步控制圈（22）与中控轮（11）之间通过同步控制杆（17）连接，同步控制圈（22）的外径与内变速器中其他内齿圈内部的棘爪部分接触。
9 、根据权利要求8所述的自行车内变速器，其特征在于：所述同步控制杆（17）插装在行星架（26）的导向槽内，其上设有与同步控制圈（22）接触的拨块。
10 、根据权利要求9所述的自行车内变速器，其特征在于：所述中控轮（11）、同步控制圈（22）以及同步控制杆（17）均设有回位弹簧。
11 、根据权利要求1-4中任一项所述的自行车内变速器，其特征在于：所述操纵组件的操纵凸轮环（4）至少其中一端设有内外两圈操纵凸起（3），所述执行组件还包括至少一根推杆（59），所述推杆（59）可沿车轮轴（18）的轴向移动，所述推杆（59）一端与设置在飞轮（6）和行星齿轮传动机构之间的离合机构连接，推杆（59）的另一端与操纵凸轮环（4）两端设置的操纵凸起接触，所述操纵凸轮环（4）一侧的车轮轴上固设有定位圈（35），其内圈设有与执行组件的杆件截面对应的凹槽用于执行组件的径向定位。
12 、根据权利要求11所述的一种自行车内变速器，其特征在于：所述行星齿轮传动机构包括并排套装在车轮轴上的两级行星齿轮传动机构，所述飞轮（6）的飞轮座（36）通过滚珠式超越离合器（28）与第一内齿圈（43）连接，并且，所述飞轮座（36）与第一行星架（42）之间设有第一离合器（37）作为动力输入连接离合器；两级行星齿轮传动机构的内齿圈之间通过内齿圈超越离合器（46）连接，其中第二级行星齿轮传动机构的内齿圈和行星架作为输出端与车轮花鼓通过超越式离合器连接。
13 、根据权利要求12所述的一种自行车内变速器，其特征在于：所述推杆（59）通过套装在车轮轴上的第一推环（39）与第一离合器（37）连接，所述第一离合器（37）通过第一离合器轴承（38）套装在第一推环（39）上，所述第一推环（39）连接有第一离合器回位弹簧（40）。
14 、根据权利要求13所述的一种自行车内变速器，其特征在于：所述中控控制杆（9）连接的离合机构为实现第一内齿圈（43）和第二行星架（51）连接和分离的第二离合器（49），所述第二离合器（49）的外圈与设置在第二内齿圈（53）内壁上可打开的第二内齿圈棘爪（52）接触，并且，所述中控控制杆（9）通过套装在车轮轴上的第二推环（48）与第二离合器（49）连接，所述第二离合器（49）通过第二离合器轴承（47）套装在第二推环（48）上，所述第二推环（48）连接有第二离合器回位弹簧（50）。
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