CN106972693B - In put motor and dispose electric bicycle of this in motor - Google Patents
In put motor and dispose electric bicycle of this in motor Download PDFInfo
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- CN106972693B CN106972693B CN201710225136.6A CN201710225136A CN106972693B CN 106972693 B CN106972693 B CN 106972693B CN 201710225136 A CN201710225136 A CN 201710225136A CN 106972693 B CN106972693 B CN 106972693B
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- ratchet
- rotating shaft
- diameter gear
- clutch
- pawl
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- 238000000926 separation method Methods 0.000 claims 1
- 238000011144 upstream manufacturing Methods 0.000 description 9
- 240000007643 Phytolacca americana Species 0.000 description 4
- 235000009074 Phytolacca americana Nutrition 0.000 description 4
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Classifications
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
- H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
- H02K7/1163—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears where at least two gears have non-parallel axes without having orbital motion
- H02K7/1166—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears where at least two gears have non-parallel axes without having orbital motion comprising worm and worm-wheel
-
- 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
- B62M6/00—Rider propulsion of wheeled vehicles with additional source of power, e.g. combustion engine or electric motor
- B62M6/40—Rider propelled cycles with auxiliary electric motor
-
- 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
- B62M6/00—Rider propulsion of wheeled vehicles with additional source of power, e.g. combustion engine or electric motor
- B62M6/40—Rider propelled cycles with auxiliary electric motor
- B62M6/45—Control or actuating devices therefor
- B62M6/50—Control or actuating devices therefor characterised by detectors or sensors, or arrangement thereof
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
- H02K7/108—Structural association with clutches, brakes, gears, pulleys or mechanical starters with friction clutches
Abstract
The application discloses put motor and dispose electric bicycle of this motor in, put motor and include including being used for connecting in the transmission of rotor and tooth dish: the clutch opening and closing control device is used for controlling the opening and closing states of the first ratchet-pawl clutch and the second ratchet-pawl clutch; the second small diameter gear is meshed with the first large diameter gear, the second medium diameter gear is meshed with the first medium diameter gear, and the second large diameter gear is meshed with the first small diameter gear. The middle motor can realize multi-gear speed change, is stable in transmission, low in noise and high in efficiency.
Description
Technical Field
The application relates to the field of motors, in particular to a middle motor and an electric bicycle provided with the middle motor.
Background
At present, the electric bicycle middle motor adopts a single-speed gear transmission structure, has low gear transmission bearing capacity and larger noise, and has relatively smaller reduction ratio (because the transmission ratio is difficult to be large in the limited design space of the electric bicycle). And the speed change mechanism is additionally arranged to realize the speed change function, the common chain-pulling structure is exposed to the outside and is corroded and damaged, and the speed change mechanism in the high-grade hub is high in price.
The present application derives from this.
Disclosure of Invention
The purpose of the application is as follows: aiming at the problems, the electric bicycle with the novel structure is provided with the middle motor, and the middle motor is stable in transmission, low in noise, large in transmission ratio, high in bearing capacity and high in efficiency, and can realize multi-gear speed change.
The technical scheme of the application is as follows: a center motor, comprising:
a motor housing;
a rotor and a stator housed in the motor housing;
a center shaft rotatably penetrating the motor housing;
a dental tray connected with the central shaft; and
a transmission device in transmission connection between the rotor and the dental tray;
the transmission device comprises:
the first rotating shaft is in transmission connection with the rotor, and the second rotating shaft is in transmission connection with the dental tray;
the first small diameter gear, the first medium diameter gear and the first large diameter gear are coaxially fixed on the first rotating shaft, and the diameters of the first small diameter gear, the first medium diameter gear and the first large diameter gear are sequentially increased;
the second small diameter gear, the second medium diameter gear and the second large diameter gear are rotatably sleeved on the second rotating shaft, the diameters of the second small diameter gear, the second medium diameter gear and the second large diameter gear are sequentially increased, the second small diameter gear is in meshed connection with the first large diameter gear, the second medium diameter gear is in meshed connection with the first medium diameter gear, and the second large diameter gear is in meshed connection with the first small diameter gear;
an overrunning clutch connecting the second large diameter gear and the second rotating shaft;
a first ratchet-pawl clutch connecting the second intermediate diameter gear and the second rotating shaft;
a second ratchet-pawl clutch connecting the second pinion gear and the second shaft; and
and a clutch engagement/disengagement control means capable of selectively bringing the first ratchet-pawl clutch and the second ratchet-pawl clutch into an engaged/disengaged state by an operation of the clutch engagement/disengagement control means.
In some preferred embodiments of the present application, the rotor is fixedly connected coaxially with the first shaft by a coupling.
In still other preferred embodiments of the present application, the clutch opening/closing control means has two driving ends respectively in contact engagement with the pawls in the first ratchet-pawl clutch and the second ratchet-pawl clutch, which selectively press/release the pawls in the first ratchet-pawl clutch and the second ratchet-pawl clutch by the action of the two driving ends, thereby bringing the first ratchet-pawl clutch and the second ratchet-pawl clutch into a disengaged/engaged state.
In still other preferred embodiments of the present application, the clutch engagement and disengagement control apparatus includes:
a shift spindle capable of pivotal movement about its own axis, disposed between the first and second ratchet-pawl clutches;
at least one group of magnetic steels, each group of magnetic steels consists of four magnetic steels, and the four magnetic steels in each group are annularly fixed on the periphery of the variable speed rotating shaft, wherein the N poles of the three magnetic steels are outwards arranged, and the S poles of the three magnetic steels are inwards arranged; the N pole of the other magnetic steel is arranged inwards, and the S pole is arranged outwards;
the first speed changing press ring is sleeved outside the second rotating shaft in an axially movable mode, the first speed changing press ring is arranged between the speed changing rotating shaft and the first ratchet pawl clutch, a pawl poking pin matched with a pawl in the first ratchet pawl clutch is fixedly arranged on the side, facing towards the first ratchet pawl clutch, of the first speed changing press ring, a first magnetic ring is fixedly arranged on the side, facing away from the first ratchet pawl clutch, of the first speed changing press ring, the N pole of the first magnetic ring faces towards the speed changing rotating shaft, and the S pole of the first magnetic ring faces towards the first speed changing press ring; and
the second variable speed press ring is coaxially sleeved outside the second rotating shaft in an axially movable mode, the second variable speed press ring is arranged between the variable speed rotating shaft and the second ratchet pawl clutch, a pawl poking pin matched with a pawl in the second ratchet pawl clutch is fixedly arranged on the side, facing towards the second ratchet pawl clutch, of the second variable speed press ring, a second magnetic ring is fixedly arranged on the side, facing away from the second ratchet pawl clutch, of the second variable speed press ring, the N pole of the second magnetic ring faces towards the variable speed rotating shaft, and the S pole of the second magnetic ring faces towards the second variable speed press ring.
In still other preferred embodiments of the present application, the second pinion and second idler gear are disposed in close proximity.
In still other preferred embodiments of the present application, the second rotating shaft is sleeved with a first pressure ring return spring clamped between the first speed changing pressure ring and the first ratchet pawl clutch, and the second rotating shaft is sleeved with a second pressure ring return spring clamped between the second speed changing pressure ring and the second ratchet pawl clutch.
In further preferred embodiments of the present application, the two speed change rotating shafts are arranged in total, and the two speed change rotating shafts are parallel to each other and symmetrically arranged at two radial sides of the second rotating shaft, and are both arranged perpendicular to the second rotating shaft; the magnetic steel is arranged in four groups, and each variable-speed rotating shaft is respectively provided with two groups of magnetic steel.
In still other preferred embodiments of the present application, the present application further includes a stepper motor, an output shaft of the stepper motor is fixedly connected to a driving gear, two variable speed rotating shafts are coaxially fixed with a driven gear respectively, and the driving gear is simultaneously meshed with the two driven gears.
In some preferred embodiments of the present application, the transmission device further includes a planar secondary torus enveloping worm gear transmission mechanism formed by a worm wheel and a worm in meshed connection, the second rotating shaft is fixedly connected with the worm coaxially through a coupling, the worm wheel is fixedly connected with the dental tray coaxially, the worm wheel is coaxially sleeved outside the central shaft, and a one-way clutch is connected between the worm wheel and the central shaft.
The electric bicycle comprises a frame, and further comprises the middle motor with the structure, wherein the motor shell is fastened with the frame.
The application has the advantages that:
1. the transmission device for connecting the rotor and the toothed disc in the middle motor adopts a three-gear speed change mechanism with very ingenious structure, can realize free switching of low speed, medium speed and high speed, is integrated into a controller and an instrument by adopting electronic speed change, and is very convenient to control.
2. The transmission gear of the three-gear speed change mechanism adopts a structure form of steel gears and nylon which are in size meshing connection, and has smooth and stable transmission and small transmission noise.
3. The transmission device for connecting the rotor and the toothed disc in the middle motor further adopts a planar secondary ring surface enveloping worm and gear transmission mechanism formed by the worm gear and the worm in meshed connection, and the planar secondary ring surface enveloping worm and gear transmission mechanism has better transmission stability, lower transmission noise, larger transmission ratio and higher bearing capacity and efficiency.
Drawings
The application is further described with reference to the accompanying drawings and examples:
FIG. 1 is an overall assembly view of a center motor in an embodiment of the present application;
FIG. 2 is an exploded view of the overall structure of a center motor in an embodiment of the present application;
FIG. 3 is an exploded view of a partial structure of a center motor in an embodiment of the present application;
FIG. 4 is a front view of the center motor of FIG. 3 partially assembled in accordance with an embodiment of the present application;
FIG. 5 is a cross-sectional view taken along the direction A-A of FIG. 4;
FIG. 6 is a side view of the center motor of FIG. 3 partially assembled in accordance with an embodiment of the present application;
FIG. 7 is a B-B sectional view of FIG. 6;
FIG. 8 is an exploded view of another partial construction of a center motor in an embodiment of the present application;
FIG. 9 is a side view of the portion of the center motor shown in FIG. 8, shown assembled, in accordance with an embodiment of the present application;
FIG. 10 is a cross-sectional view taken along the direction C-C of FIG. 9;
FIG. 11 is an exploded view of yet another partial construction of a central motor in an embodiment of the present application;
FIG. 12 is an exploded view of a first shaft according to an embodiment of the present application;
FIG. 13 is an assembly view of a first shaft according to an embodiment of the present disclosure;
FIG. 14 is a schematic view of a partial structure of a center motor in a low speed transmission mode according to an embodiment of the present application;
FIG. 15 is an axial view of the shift spindle of FIG. 14 with the right rectangular box showing the magnetic ring on the first shift collar and the left rectangular box showing the magnetic ring on the second shift collar;
fig. 16 is a schematic view of a partial structure of a mid-motor in a medium speed transmission mode according to an embodiment of the present application;
FIG. 17 is an axial view of the shift spindle of FIG. 16 with the right rectangular box showing the magnetic ring on the first shift collar and the left rectangular box showing the magnetic ring on the second shift collar;
FIG. 18 is a schematic view of a partial structure of a center motor in a high speed transmission mode according to an embodiment of the present application;
FIG. 19 is an axial view of the shift spindle of FIG. 18 with the right rectangular box showing the magnetic ring on the first shift collar and the left rectangular box showing the magnetic ring on the second shift collar;
wherein: 1-motor housing, 2-rotor, 3-stator, 4-central shaft, 5-tooth disc, 6-worm wheel, 7-worm, 8-one-way clutch, 9-first deep groove ball bearing, 10-second deep groove ball bearing, 11-first tapered roller bearing, 12-second tapered roller bearing, 13-crank, 14-stepper motor, 15-driven gear, 16-left face cover, 17-right face cover, 18-pedal, 19-first rotating shaft, 20-second rotating shaft, 21-first small diameter gear, 22-first intermediate diameter gear, 23-first large diameter gear, 24-second small diameter gear, 25-second intermediate diameter gear, 26-second large diameter gear, 27-overrunning clutch, 28-first ratchet pawl clutch, 29-second ratchet pawl clutch, 30-speed change rotating shaft, 31-magnetic steel, 32-first speed change press ring, 33-pawl pin, 34-magnetic ring, 35-second speed change, 36-first limit check ring, 37-second limit ring, 38-first coupler, 39-second hall-ring, 40-second coupler, reset spring press ring, 43-second coupler, reset spring press ring, and inductor-press ring.
Detailed Description
Fig. 1 to 19 show a preferred embodiment of a central motor of the type described herein, which, like a driven central motor, also comprises: the motor comprises a motor shell 1, a rotor 2 and a stator 3 which are accommodated in the motor shell, a central shaft 4 which is rotatably arranged in the motor shell in a penetrating way, and a toothed disc 5 which is connected with the central shaft (the toothed disc and the central shaft are not directly fastened and connected, but are indirectly connected through a one-way clutch and a worm gear) and a transmission device which is connected between the rotor 2 and the toothed disc 5 in a transmission way. An induction magnetic ring 42 is fixed on the center shaft 4, and a Hall sensor 43 corresponding to the induction magnetic ring is fixed in the motor shell 1.
In practical application, the two ends of the center shaft 4 are connected with the cranks 13, pedals 18 are arranged on the cranks, the chain wheel 5 is connected with a chain connected with a rear flywheel of the bicycle, and the motor shell 1 is fixedly connected with a frame of the electric bicycle.
A key improvement of this embodiment is that, referring to fig. 1-7, the above-mentioned transmission no longer employs a conventional simple planetary gear reduction transmission structure, and the transmission includes: the plane secondary torus enveloping worm gear and worm drive mechanism is composed of a worm wheel 6 and a worm 7 which are connected in a meshed manner.
The planar secondary torus enveloping worm and gear transmission mechanism is different from a common worm and gear mechanism, has better transmission stability, lower transmission noise, larger transmission ratio and higher bearing capacity and efficiency. The tooth surface lubrication angle is large, and the formation and the retention of a dynamic pressure oil film are good.
The worm 7 described above can be connected directly to the rotor 2 or indirectly to the rotor 2 via a corresponding transmission element. The worm wheel 6 can be directly connected with the toothed disc 5 or can be indirectly connected with the toothed disc 5 through corresponding driving members. In the present embodiment, the worm 7 is indirectly connected to the rotor 2 via a corresponding transmission member, and the worm wheel 6 is indirectly connected to the toothed disc 5 via a corresponding transmission member.
When the motor is powered on to drive the rotor 2 to rotate, the rotor transmits rotary motion to the worm 7 through the corresponding transmission part, the worm 7 drives the worm wheel 6 meshed with the worm 7 to rotate, the worm wheel 6 drives the tooth disc 5 to rotate through the downstream transmission part, and the tooth disc 5 drives the wheels to rotate through the chain, so that the vehicle moves forwards.
In this embodiment, the central shaft 4 and the dental tray 5 are actually connected by means of the worm wheel 6, specifically: the worm wheel 6 is coaxially sleeved outside the center shaft 4, a one-way clutch 8 is connected between the worm wheel 6 and the center shaft, and the worm wheel 6 and the toothed disc 5 are coaxially and fixedly connected through a spline. Reference is made to fig. 5.
When the pedal is stepped on by manpower and the middle shaft 4 is driven to rotate by the crank, the induction magnetic ring on the middle shaft 4 rotates, and after the Hall sensor senses the rotation of the induction magnetic ring, the motor is started, and the bicycle is in a power-assisted mode. In the power-assisted mode, the pedaling force of the rider is sequentially transmitted to the chain wheel 5 through the pedals, the crank, the middle shaft, the one-way clutch and the worm wheel, and then transmitted to the rear wheel of the bicycle through a chain connected with the chain wheel 5.
Under the pure manpower mode of riding, the rider steps on the pedal and drives the axis 4 through the crank and rotate, one-way clutch 8 is in the locking state, axis 4 drives worm wheel 6 through one-way clutch 8 and rotates (the rotation of worm wheel 6 also can transmit for worm 7, only need set up the clutch between rotor 2 and worm 7 and can avoid worm 7 to transmit this rotary motion for rotor 2), worm wheel 6 drives tooth dish 5 again, tooth dish 5 drives the bicycle rear wheel through the chain and rotates, makes the vehicle forward.
In the process that the motor rotor drives the worm 7 and then the worm 7 drives the worm wheel 6 to rotate. The presence of the force and the reaction force due to the meshing engagement of the worm 7 and the worm wheel 6 results in that both the worm 7 and the worm wheel 6 are subjected to thrust in the axial direction. Specifically, in fig. 5, the worm 7 receives a leftward thrust, and the worm wheel 6 receives a thrust directed perpendicularly to the straight outward.
In order to solve the above-described problems, in the present embodiment, a first tapered roller bearing 11 supported in the motor housing 1 is coaxially connected to the worm 7, and a second tapered roller bearing 12 supported in the motor housing 1 is coaxially connected to the worm wheel 6. The axial thrust force applied to the worm 7 and the worm wheel 6 is resisted by the first tapered roller bearing 11 and the second tapered roller bearing 12. Wherein, the model of the first tapered roller bearing 11 is 30202, and the model of the second tapered roller bearing 12 is 32908.
The first tapered roller bearing 11 and the second tapered roller bearing 12 are assembled in the following manner:
the bearing inner ring of the first tapered roller bearing 11 is coaxially sleeved outside the worm 7 and is fixedly connected with the worm 7 through a clamp spring, and the bearing outer ring of the first tapered roller bearing 11 is relatively fixed with the motor shell 1 (the bearing outer ring and the motor shell can be directly and fixedly connected and can also be indirectly fixed through a transition piece).
The axial one end face of the worm wheel 6 is provided with a bearing accommodating cavity extending inwards along the axial direction of the worm wheel, the bearing outer ring of the second tapered roller bearing 12 is embedded in the bearing accommodating cavity and is fixed with the worm wheel 6, and the bearing inner ring of the second tapered roller bearing 12 is fixed relative to the motor housing 1 (the bearing inner ring and the motor housing can be directly and fixedly connected and can also be indirectly fixed through a transition piece).
In order to ensure the stability of the assembly positions of the worm 7 and the worm wheel 6 in the motor housing 1 and prevent deflection and deflection caused by stress on the worm 7 and the worm wheel 6, the first deep groove ball bearing 9 supported in the motor housing 1 is coaxially connected to the worm 7, and the second deep groove ball bearing 10 supported in the motor housing 1 is coaxially connected to the worm wheel 6. The first deep groove ball bearing 9 and the first tapered roller bearing 11 are axially spaced apart, and the second deep groove ball bearing 10 and the second tapered roller bearing 12 are axially spaced apart, thus stably supporting the worm 7 and the worm wheel 6.
In view of the long and slender structure of the worm 7, the first deep groove ball bearing 9 and the first tapered roller bearing 11 are respectively connected to two axial ends of the worm 7, so that stability of the assembly position of the worm is better ensured.
Referring to fig. 1, in order to facilitate the installation and fixation of the center motor on the bicycle frame, a motor cover is further provided, in which the motor housing 1 is fixedly accommodated, and which is composed of a left cover 16 and a right cover 17 fastened and fixed together by screws, so that the accommodation and fixation of the motor housing 1 by the motor cover are facilitated. A plurality of motor connecting holes are formed in the motor cover, and during practical application, the motor lock is fastened on the bicycle frame by bolts penetrating into the motor connecting holes.
The above description describes that the transmission device for connecting the rotor 2 and the tooth disc 5 in the central motor comprises a planar secondary torus enveloping worm gear transmission mechanism formed by a worm wheel 6 and a worm 7, and describes that the worm 7 is connected with the rotor 2 through an upstream transmission member, the worm wheel 6 is connected with the tooth disc 5 through a downstream transmission member, and further describes the structural form of the downstream transmission member, and the specific structure of the upstream transmission member is not described.
It will be appreciated that the above-mentioned upstream, downstream and planar secondary torus enveloping worm gear drive together form a drive for connection to the rotor 2 and the tooth disc 5.
Before describing the specific structure of the upstream transmission member in this embodiment, it should be noted that the upstream transmission member may take various forms known to those skilled in the art, such as a common gear transmission structure, a chain transmission structure, or a belt transmission structure.
In the following, referring to fig. 8-19, the structure of the upstream transmission member for connecting the worm 7 of the rotor 2 in this embodiment is described in detail, wherein the upstream transmission member is a component of the transmission device for connecting the rotor 2 and the dental tray 5, and includes a first rotating shaft 19 and a second rotating shaft 20 arranged in parallel, the first rotating shaft 19 is coaxially and fixedly connected with the rotor 2 (in particular, the rotor shaft of the rotor) through a first coupling 38, and the second rotating shaft 20 is coaxially and fixedly connected with the worm 7 through a second coupling 39. The first rotary shaft 19 is coaxially and fixedly provided with a first small diameter gear 21, a first medium diameter gear 22 and a first large diameter gear 23 which are distributed at intervals in the axial direction of the first rotary shaft and sequentially increase in diameter. In the present embodiment, the first small diameter gear 21, the first intermediate diameter gear 22, and the first large diameter gear 23 are formed integrally with the first rotary shaft 19, that is, the first small diameter gear 21, the first intermediate diameter gear 22, and the first large diameter gear 23 are three shaft teeth having different diameters formed on the first rotary shaft 19. More specifically, referring to fig. 12 and 13, the first rotating shaft 19 is formed by connecting three separate shaft segments, and the first small diameter gear 21, the first medium diameter gear 22 and the first large diameter gear 23 are integrally formed on the three shaft segments, respectively. The second rotating shaft 20 is rotatably sleeved with a second small diameter gear 24, a second medium diameter gear 25 and a second large diameter gear 26 which are distributed at intervals along the axial direction of the second rotating shaft and sequentially increase in diameter. The second intermediate diameter gear 25 and the second rotating shaft 20 are connected by a first ratchet-pawl clutch 28, the second small diameter gear 24 and the second rotating shaft 20 are connected by a second ratchet-pawl clutch 29, and the second large diameter gear 26 and the second rotating shaft 20 are connected by an overrunning clutch 27. In order to ensure the position stability of the second small diameter gear 24, the second intermediate diameter gear 25 and the second large diameter gear 26 on the second rotating shaft 20 and improve the service lives of the first ratchet pawl clutch 28, the second ratchet pawl clutch 29 and the overrunning clutch 27, in this embodiment, a support bearing is respectively arranged between the second small diameter gear 24 and the second rotating shaft 20, between the second intermediate diameter gear 25 and the second rotating shaft 20, and between the second large diameter gear 26 and the second rotating shaft 20. The first small diameter gear 21 is meshed with the second large diameter gear 26, and the first small diameter gear 21 drives the second large diameter gear 26 to rotate during operation, so that low-speed transmission from the first rotating shaft to the second rotating shaft is realized. The first pitch diameter gear 22 is meshed with the second pitch diameter gear 25, and the second pitch diameter gear 25 is driven to rotate by the first pitch diameter gear 22 during operation, so that the first rotation shaft and the second rotation shaft realize medium-speed transmission. The first large-diameter gear 23 is meshed with the second small-diameter gear 24, and the first large-diameter gear 23 drives the second small-diameter gear 24 to rotate during operation, so that high-speed transmission from the first rotating shaft to the second rotating shaft is realized. And a clutch on-off control means is provided, by the operation of which the first ratchet-pawl clutch 28 and the second ratchet-pawl clutch 29 can be selectively brought into the off/on state, respectively.
When the motor is powered on to drive the rotor 2 to rotate, the rotor 2 drives the first rotating shaft 19 connected with the motor to rotate, and the first small-diameter gear 21, the first medium-diameter gear 22 and the first large-diameter gear 23 integrally fixed on the first rotating shaft 19 synchronously rotate along with the first small-diameter gear (the rotation angular speeds of the three are the same), so that the second large-diameter gear 26, the second medium-diameter gear 25 and the second small-diameter gear 24 are driven to mesh and rotate.
In the low speed mode, the first ratchet-pawl clutch 28 and the second ratchet-pawl clutch 29 are both in a disengaged state by the operation of the clutch engagement/disengagement control means, and only the overrunning clutch 27 is in an operating state (the overrunning clutch 27 is not affected by the clutch engagement/disengagement control means). Therefore, the rotational torque of the second small diameter gear 24 and the second intermediate diameter gear 25 is not transmitted to the second rotating shaft 20, and the second small diameter gear 24 and the second intermediate diameter gear 25 "slip" on the second rotating shaft 20. Only the rotation of the second large diameter gear 26 is synchronously transmitted to the second rotating shaft 20, so that the second rotating shaft 20 rotates along with the second large diameter gear 26 at the same angular velocity, and the second rotating shaft 20 transmits the rotation motion to the downstream worm 7, worm wheel 6 and tooth disc 5. Low-speed travel of the vehicle is achieved.
In the medium speed mode, the first ratchet-pawl clutch 28 is engaged by the operation of the clutch on-off control device, and the second ratchet-pawl clutch 29 is disengaged (the overrun clutch 27 is not affected by the clutch on-off control device). Therefore, the rotational torque of the second small diameter gear 24 is not transmitted to the second rotating shaft 20, and the second small diameter gear 24 "slips" on the second rotating shaft 20. Because the rotational angular velocity of the second intermediate diameter gear 25 is greater than the angular velocity of the second large diameter gear 26, the second intermediate diameter gear 25 drives the second rotating shaft 20 to rotate faster than the angular velocity of the second large diameter gear 26, so that the overrunning clutch 27 between the second large diameter gear 26 and the second rotating shaft 20 is in a disengaged state, and the second large diameter gear 26 is also in a "slipping" state on the second rotating shaft 20. In this way, only the rotation of the second pitch diameter gear 25 is synchronously transmitted to the second rotating shaft 20, and the second rotating shaft 20 transmits the rotation to the worm 7, the worm wheel 6 and the tooth disc 5 at the downstream. The medium-speed running of the vehicle is realized.
In the high speed mode, the second ratchet-pawl clutch 29 is engaged by the operation of the clutch on-off control device, and the first ratchet-pawl clutch 28 is disengaged (the overrun clutch 27 is not affected by the clutch on-off control device). Therefore, the rotational torque of the second intermediate diameter gear 25 is not transmitted to the second rotating shaft 20, and the second intermediate diameter gear 25 "slips" on the second rotating shaft 20. Similarly, since the rotational angular velocity of the second small diameter gear 24 is greater than the angular velocity of the second large diameter gear 26, the second small diameter gear 24 drives the second rotating shaft 20 to rotate faster than the second large diameter gear 26, so that the overrunning clutch 27 between the second large diameter gear 26 and the second rotating shaft 20 is in a disengaged state, and the second large diameter gear 26 is also in a "slipping" state on the second rotating shaft 20. In this way, only the rotation of the second small diameter gear 24 is simultaneously transmitted to the second rotating shaft 20, and the second rotating shaft 20 transmits the rotation to the downstream worm 7, worm wheel 6 and toothed disc 5. High-speed travel of the vehicle is achieved.
The clutch opening/closing control device has two driving ends respectively in contact fit with the pawls in the first ratchet-pawl clutch 28 and the second ratchet-pawl clutch 29, and selectively presses/releases the pawls in the first ratchet-pawl clutch 28 and the second ratchet-pawl clutch 29 by the actions of the two driving ends, so that the first ratchet-pawl clutch 28 and the second ratchet-pawl clutch 29 are in an open/closed state.
More specifically, the clutch engagement/disengagement control apparatus described above mainly includes: two variable speed rotating shafts 30, sixteen magnetic steels 31, a first variable speed pressing ring 32 and a second variable speed pressing ring 35.
The two shift rotating shafts 30 are parallel to each other and symmetrically arranged on both radial sides of the second rotating shaft 20 and perpendicular to the second rotating shaft 20, while the two shift rotating shafts 30 are arranged at positions between the first ratchet-pawl clutch 28 and the second ratchet-pawl clutch 29. The shift spindle 30 is pivotally movable about its own axis.
Sixteen magnetic steels 31 are equally divided into four groups, each group is four, and two groups of magnetic steels 31 are arranged on each variable-speed rotating shaft 30. Specifically, four magnetic steels 31 in each group are fixed on the speed change rotating shaft 30 and distributed annularly around the speed change rotating shaft 30. Wherein the N poles of the three magnetic steels 31 are arranged outward and the S poles are arranged inward. The N pole of the other magnetic steel 31 is disposed inward, and the S pole is disposed outward. The two groups of magnetic steel 31 on each speed-changing rotating shaft 30 are vertically symmetrical.
The first gear-shifting pressure ring 32 is coaxially and axially movably sleeved outside the second rotating shaft 20, and is arranged between the gear-shifting rotating shaft 30 and the first ratchet-pawl clutch 28, a pawl poking pin 33 matched with a pawl in the first ratchet-pawl clutch 28 is fixedly arranged on the side of the first gear-shifting pressure ring 32 facing the first ratchet-pawl clutch 28, a magnetic ring 34 is fixedly arranged on the side of the first gear-shifting pressure ring 32 facing away from the first ratchet-pawl clutch 28, the N pole of the magnetic ring 34 is arranged towards the gear-shifting rotating shaft 30, and the S pole is arranged towards the first gear-shifting pressure ring 32 (namely, the S pole is arranged towards the first ratchet-pawl clutch 28).
The second speed changing pressure ring 35 is coaxially sleeved outside the second rotating shaft 20 in an axially movable manner, and is arranged between the speed changing rotating shaft 30 and the second ratchet pawl clutch 29, the side of the second speed changing pressure ring 35 facing the second ratchet pawl clutch 29 is fixedly provided with a pawl poking pin 33 matched with a pawl in the second ratchet pawl clutch 29, the side of the second speed changing pressure ring 35 facing away from the second ratchet pawl clutch 29 is fixedly provided with a magnetic ring 34, the N pole of the magnetic ring 34 is arranged towards the speed changing rotating shaft 30, and the S pole is arranged towards the second ratchet pawl clutch 29 (namely, the S pole is arranged towards the second ratchet pawl clutch 29).
In the low speed mode, the speed change shaft 30 rotates to the state shown in fig. 14 and 15, and the magnetic steel 31 closest to the first speed change pressure ring 32 and the magnetic steel 31 closest to the second speed change pressure ring 35 on the speed change shaft 30 are all arranged with their N poles facing outwards, so that repulsive force exists between the magnetic steel of the speed change shaft and the magnetic rings 34 fixed on the first speed change pressure ring 32 and the second speed change pressure ring 35. The repulsive force pushes the first gear-shifting pressure ring 32 to press the first ratchet-pawl clutch 28, so that the pawl poking pin 33 on the first gear-shifting pressure ring 32 pushes and pokes the pawl in the first ratchet-pawl clutch 28 to retract (the pawl retracts against the elastic force of the pawl spring), the pawl in the first ratchet-pawl clutch 28 is disengaged from the ratchet, and the first ratchet-pawl clutch 28 is in a disengaged state. The repulsive force pushes the second gear shift pressing ring 35 to press the second ratchet pawl clutch 29, so that the pawl poking pin 33 on the second gear shift pressing ring 35 pushes and pokes the pawl in the second ratchet pawl clutch 29 to retract (the pawl retracts against the elastic force of the pawl spring), the pawl in the second ratchet pawl clutch 29 is disengaged from the ratchet, and the second ratchet pawl clutch 29 is in a disengaged state.
In the medium speed mode, the shift spindle 30 rotates to the state shown in fig. 16 and 17. The S pole of the magnetic steel 31 closest to the first speed changing pressing ring 32 on the speed changing rotating shaft 30 is arranged outwards, and attractive force exists between the S pole and the magnetic ring 34 on the first speed changing pressing ring 32. The attractive force pulls the first speed changing pressure ring 32 to move away from the first ratchet pawl clutch 28, so that the pawl poking pin 33 on the first speed changing pressure ring 32 is separated from the pawl in the first ratchet pawl clutch 28, the pawl in the first ratchet pawl clutch 28 is normally ejected to be matched with the ratchet under the action of the pawl elastic force, and the first ratchet pawl clutch 28 is in an engaged state. The N pole of the magnetic steel 31 closest to the second speed changing pressing ring 35 on the speed changing rotating shaft 30 is arranged outwards, and repulsive force exists between the N pole and the magnetic ring 34 on the second speed changing pressing ring 35. The repulsive force pushes the second gear shift pressing ring 35 to press the second ratchet and pawl clutch 29, so that the pawl poking pin 33 on the second gear shift pressing ring 35 pokes the pawl in the second ratchet and pawl clutch 29 to retract (the pawl retracts against the elastic force of the pawl spring), the pawl in the second ratchet and pawl clutch 29 is disengaged from the ratchet, and the second ratchet and pawl clutch 29 is in a disengaged state.
In the high speed mode, the shift spindle 30 rotates to the state shown in fig. 18 and 19. The S pole of the magnetic steel 31 closest to the second variable speed pressing ring 35 on the variable speed rotating shaft 30 is arranged outwards, and attractive force exists between the S pole and the magnetic ring 34 on the second variable speed pressing ring. The attractive force pulls the second speed changing pressure ring to move away from the second ratchet pawl clutch 29, so that the pawl poking pin 33 on the second speed changing pressure ring is separated from the pawl in the second ratchet pawl clutch 29, the pawl in the second ratchet pawl clutch 29 is normally ejected to be matched with the ratchet under the action of the pawl elastic force, and the second ratchet pawl clutch 29 is in an engaged state. The N pole of the magnetic steel 31 closest to the first speed changing pressing ring 32 on the speed changing rotating shaft 30 is arranged outwards, and repulsive force exists between the N pole and the magnetic ring 34 on the first speed changing pressing ring 32. The repulsive force pushes the first gear-shifting pressure ring 32 to press the first ratchet-pawl clutch 28, so that the pawl poking pin 33 on the first gear-shifting pressure ring 32 pokes the pawl in the first ratchet-pawl clutch 28 to retract (the pawl retracts against the elastic force of the pawl spring), the pawl of the first ratchet-pawl clutch 28 is disengaged from the ratchet, and the first ratchet-pawl clutch 28 is in a disengaged state.
In order to ensure that the repulsive force and attractive force of the magnetic steel on the shift spindle 30 to the first shift pressing ring 32 and the second shift pressing ring 35 are sufficiently large, it is preferable to arrange the second small diameter gear 24 and the second medium diameter gear 25 in close proximity, and the second large diameter gear 26 is arranged at the extreme ends of the three gears (the second small diameter gear 24, the second medium diameter gear 25 and the second large diameter gear 26), that is, the second large diameter gear 26 is preferably not arranged at a position between the second small diameter gear 24 and the second medium diameter gear 25.
It can be seen that the two driving ends of the clutch opening and closing control device are respectively a pawl poking pin 33 on the first speed changing press ring 32 and a pawl poking pin 33 on the second speed changing press ring 35.
In addition, in this embodiment, a first pressure ring return spring 40 is provided on the second rotating shaft 20 so as to be sandwiched between the first speed changing pressure ring 32 and the first ratchet-pawl clutch 28, and a second pressure ring return spring 41 is provided on the second rotating shaft 20 so as to be sandwiched between the second speed changing pressure ring 35 and the second ratchet-pawl clutch 29. So that the first gear shifting press ring 32 and the second gear shifting press ring 35 can move towards the direction of the gear shifting rotating shaft 30 under the elastic force of the return spring when the magnetic attraction force is received (or the magnetic force is not received), and the pawl poking pin 33 on the first gear shifting press ring and the second gear shifting press ring are separated from the wheel pawl clutch, so that the first ratchet pawl clutch 28 or the second ratchet pawl clutch 29 is in an engaged state. The reset spring and the magnetic repulsive force act together to drive the speed changing compression ring to move away from the wheel pawl clutch.
The number of the variable speed rotating shafts 30 can be one, three or four, and the number of the variable speed rotating shafts 30 is two in the embodiment, and four groups of eight magnetic steels are arranged on each variable speed rotating shaft 30 to ensure that the magnetic steels on the variable speed rotating shaft 30 have symmetry on repulsive force or attractive force generated by the variable speed crushing of the upper magnetic ring. In some other embodiments of the present application, only one set of the magnetic steel 31 with the above structure may be disposed on each of the variable speed rotating shafts 30.
Further, in order to prevent the first shift pressing ring 32 and the second shift pressing ring 35 from contacting the shift spindle 30 under the action of the magnetic attraction force, the rotation of the shift spindle 30 is disturbed. The second rotating shaft 20 is fixedly sleeved with: a first limit check ring 36 positioned between the speed change rotating shaft 30 and the first speed change pressing ring 32, and a second limit check ring 37 positioned between the speed change rotating shaft 30 and the second speed change pressing ring 35. The first gear shifting press ring 32 and the second gear shifting press ring 35 are respectively blocked outside the gear shifting rotating shaft 30 by the first limiting check ring 36 and the second limiting check ring 37.
In addition, the second small diameter gear 24, the second intermediate diameter gear 25 and the second large diameter gear 26 are all nylon gears, so that noise generated in the process of meshing the first small diameter gear 21, the first intermediate diameter gear 22, the first large diameter gear 23, the second large diameter gear 26, the second intermediate diameter gear 25 and the second small diameter gear 24 can be greatly reduced, and mute transmission is basically realized. The first rotating shaft 19 and the first small diameter gear 21, the first intermediate diameter gear 22 and the first large diameter gear 23 thereon are all made of steel.
As shown in fig. 11, the rotation of the speed change shaft 30 can be realized by providing a corresponding circuit, or can be realized by providing a full mechanical transmission part and totally relying on manpower. In this embodiment, the rotation of the variable speed rotating shaft 30 is driven by a micro stepping motor 14, the output shaft of the stepping motor 14 is fixedly connected with a driving gear, two variable speed rotating shafts 30 are respectively coaxially fixed with a driven gear 15, the driving gear is simultaneously meshed with the two driven gears 15 to drive the two variable speed rotating shafts 30 to synchronously rotate, a control circuit of the micro stepping motor 14 is integrated into a master controller of the middle motor, and the master controller is connected with a handlebar instrument during practical application and is convenient to operate and control.
For the convenience of the reader to understand the technical solution of the present application more conveniently, we call the upstream transmission member of this structure connecting the worm 7 and the rotor 2 as a three-gear (high, medium and low) gear change mechanism.
It will be apparent to those skilled in the art that in some other embodiments of the present application, the upstream end of the planar secondary torus envelope worm gear mechanism (worm wheel 6 and worm 7) may be provided with other types of driving members for connecting the rotor 2 and worm 7, and is not limited to the three-speed gear shifting mechanism described in the present embodiment. Also, in other embodiments of the present application, the downstream end of the three-gear transmission mechanism may be provided with other types of transmission members for connecting the tooth disc 5 of the second shaft 20, which are not limited to the planar secondary torus enveloping worm gear mechanism described in the present embodiment.
The foregoing embodiments are merely illustrative of the technical concept and features of the present application, and are intended to enable people to understand the content of the present application and implement the same, not to limit the protection scope of the present application. All equivalent changes or modifications made according to the spirit of the main technical solutions of the present application should be covered in the protection scope of the present application.
Claims (8)
1. A center motor, comprising:
a motor housing (1);
a rotor (2) and a stator (3) housed in the motor housing;
a center shaft (4) rotatably penetrating the motor shell;
a dental tray (5) connected with the central shaft; and
a transmission device connected between the rotor (2) and the dental tray (5);
the transmission device is characterized by comprising:
a first rotating shaft (19) and a second rotating shaft (20) which are arranged in parallel, wherein the first rotating shaft (19) is in transmission connection with the rotor (2), and the second rotating shaft (20) is in transmission connection with the dental tray (5);
a first small diameter gear (21), a first medium diameter gear (22) and a first large diameter gear (23) which are coaxially fixed on the first rotating shaft (19) and sequentially increase in diameter;
the second small diameter gear (24), the second medium diameter gear (25) and the second large diameter gear (26) are rotatably sleeved on the second rotating shaft (20) and sequentially increased in diameter, the second small diameter gear (24) is meshed with the first large diameter gear (23), the second medium diameter gear (25) is meshed with the first medium diameter gear (22), and the second large diameter gear (26) is meshed with the first small diameter gear (21);
an overrunning clutch (27) connecting the second large diameter gear (26) and the second rotating shaft (20);
a first ratchet-pawl clutch (28) connecting the second intermediate diameter gear (25) and the second rotating shaft (20);
a second ratchet-pawl clutch (29) connecting the second small-diameter gear (24) and the second rotating shaft (20); and
a clutch opening/closing control device that can selectively bring the first ratchet-pawl clutch and the second ratchet-pawl clutch into any one of three states by an operation of the clutch opening/closing control device:
the first ratchet-pawl clutch is engaged and the second ratchet-pawl clutch is disengaged;
the first ratchet-pawl clutch is disengaged and the second ratchet-pawl clutch is engaged;
the first ratchet-pawl clutch and the second ratchet-pawl clutch are both disengaged;
the clutch opening and closing control device is provided with two driving ends respectively in contact fit with pawls in the first ratchet-pawl clutch (28) and the second ratchet-pawl clutch (29), and the two driving ends can selectively press/release the pawls in the first ratchet-pawl clutch (28) and the second ratchet-pawl clutch (29) through the actions of the two driving ends so as to enable the first ratchet-pawl clutch (28) and the second ratchet-pawl clutch (29) to be in a separation/connection state;
the clutch engagement/disengagement control apparatus includes:
a speed change shaft (30) capable of pivotal movement about its own axis, disposed between the first ratchet-pawl clutch (28) and the second ratchet-pawl clutch (29);
at least one group of magnetic steels (31), each group is composed of four magnetic steels (31), and the four magnetic steels (31) in each group are annularly fixed on the periphery of the speed change rotating shaft (30), wherein the N poles of the three magnetic steels (31) are outwards arranged, and the S poles of the three magnetic steels are inwards arranged; the N pole of the other magnetic steel (31) is arranged inwards, and the S pole is arranged outwards;
the first speed changing press ring (32) is sleeved outside the second rotating shaft (20) in an axially movable mode, the first speed changing press ring (32) is arranged between the speed changing rotating shaft (30) and the first ratchet pawl clutch (28), a pawl poking pin (33) matched with a pawl in the first ratchet pawl clutch (28) is fixedly arranged on the side, facing towards the first ratchet pawl clutch, of the first speed changing press ring (32), a first magnetic ring is fixedly arranged on the side, facing away from the first ratchet pawl clutch (28), of the first speed changing press ring (32), the N pole of the first magnetic ring is arranged towards the speed changing rotating shaft, and the S pole of the first magnetic ring is arranged towards the first speed changing press ring; and
the second speed changing press ring (35) is coaxially sleeved outside the second rotating shaft (20) in an axially movable mode, the second speed changing press ring (35) is arranged between the speed changing rotating shaft (30) and the second ratchet pawl clutch (29), a pawl poking pin matched with a pawl in the second ratchet pawl clutch (29) is fixedly arranged on the side, facing towards the second ratchet pawl clutch (29), of the second speed changing press ring (35), a second magnetic ring is fixedly arranged on the side, facing away from the second ratchet pawl clutch (29), of the second speed changing press ring, the N pole of the second magnetic ring faces towards the speed changing rotating shaft, and the S pole of the second magnetic ring faces towards the second speed changing press ring.
2. A mid-motor according to claim 1, characterized in that the rotor (2) is fixedly connected coaxially with the first shaft (19) by means of a coupling.
3. A mid-motor according to claim 1, characterized in that the second small diameter gear (24) and the second medium diameter gear (25) are arranged in close proximity.
4. The centrally-mounted motor according to claim 1, wherein the second rotating shaft (20) is sleeved with a first compression ring return spring (40) clamped between the first speed changing compression ring (32) and the first ratchet pawl clutch (28), and the second rotating shaft (20) is sleeved with a second compression ring return spring (41) clamped between the second speed changing compression ring (35) and the second ratchet pawl clutch (29).
5. The centrally-mounted motor according to claim 1, characterized in that the two variable-speed rotating shafts (30) are provided in total, the two variable-speed rotating shafts (30) are mutually parallel and symmetrically arranged on both radial sides of the second rotating shaft (20), and at the same time, the two variable-speed rotating shafts (30) are arranged perpendicular to the second rotating shaft (20); four groups of magnetic steels (31) are arranged in total, and two groups of magnetic steels (31) are respectively arranged on each variable-speed rotating shaft (30).
6. The centrally-mounted motor according to claim 5, further comprising a stepper motor (14), wherein an output shaft of the stepper motor is fixedly connected with a driving gear, two variable speed rotating shafts (30) are respectively coaxially fixed with a driven gear (15), and the driving gear is simultaneously meshed with the two driven gears (15).
7. The centrally-mounted motor according to claim 1, wherein the transmission device further comprises a planar secondary torus enveloping worm gear transmission mechanism formed by a worm wheel (6) and a worm (7) which are in meshed connection, the second rotating shaft (20) is fixedly connected with the worm (7) coaxially through a coupler, the worm wheel (6) is fixedly connected with the toothed disc (5) coaxially, the worm wheel (6) is coaxially sleeved outside the center shaft (4), and a one-way clutch (8) is connected between the worm wheel (6) and the center shaft (4).
8. An electric bicycle comprising a frame, characterized in that it further comprises a centrally mounted electric motor as claimed in any one of claims 1-7, said electric motor housing (1) being fastened to said frame.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN201710225136.6A CN106972693B (en) | 2017-04-07 | 2017-04-07 | In put motor and dispose electric bicycle of this in motor |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201710225136.6A CN106972693B (en) | 2017-04-07 | 2017-04-07 | In put motor and dispose electric bicycle of this in motor |
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| CN106972693B true CN106972693B (en) | 2024-04-05 |
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| CN201710225136.6A Active CN106972693B (en) | 2017-04-07 | 2017-04-07 | In put motor and dispose electric bicycle of this in motor |
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Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108082369A (en) * | 2017-12-28 | 2018-05-29 | 广东东辉恒力电机有限公司 | Electric bicycle and electric bicycle component |
| CN110181996A (en) * | 2018-02-23 | 2019-08-30 | 德安百世实业股份有限公司 | Magnetic force controls suitching type flower hub |
| CN110406623A (en) * | 2019-08-20 | 2019-11-05 | 浙江科技学院 | A kind of electric bicycle overdrive clutch non-clashing gear set |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2898447Y (en) * | 2006-02-27 | 2007-05-09 | 苏州奔集动力有限公司 | Electrically-controlled speed variator |
| CN106428394A (en) * | 2016-09-07 | 2017-02-22 | 新安乃达驱动技术（上海）股份有限公司 | Electric aided-bicycle, as well as built-in motor drive system and control method thereof |
| CN206727820U (en) * | 2017-04-07 | 2017-12-08 | 黄善劲 | A kind of built-in motor and the electric bicycle for configuring the built-in motor |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101422135B1 (en) * | 2012-08-09 | 2014-07-22 | (주)엠비아이 | Automatic transmission |
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2017
- 2017-04-07 CN CN201710225136.6A patent/CN106972693B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2898447Y (en) * | 2006-02-27 | 2007-05-09 | 苏州奔集动力有限公司 | Electrically-controlled speed variator |
| CN106428394A (en) * | 2016-09-07 | 2017-02-22 | 新安乃达驱动技术（上海）股份有限公司 | Electric aided-bicycle, as well as built-in motor drive system and control method thereof |
| CN206727820U (en) * | 2017-04-07 | 2017-12-08 | 黄善劲 | A kind of built-in motor and the electric bicycle for configuring the built-in motor |
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