CN103661761B - Bicycle drive unit - Google Patents
Bicycle drive unit Download PDFInfo
- Publication number
- CN103661761B CN103661761B CN201310401627.3A CN201310401627A CN103661761B CN 103661761 B CN103661761 B CN 103661761B CN 201310401627 A CN201310401627 A CN 201310401627A CN 103661761 B CN103661761 B CN 103661761B
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- China
- Prior art keywords
- gear
- driver element
- motor
- bicycle
- combining unit
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Classifications
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- 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
- B62M6/55—Rider propelled cycles with auxiliary electric motor power-driven at crank shafts parts
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- 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
- B62M11/145—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 bottom bracket
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D41/00—Freewheels or freewheel clutches
- F16D41/24—Freewheels or freewheel clutches specially adapted for cycles
- F16D41/30—Freewheels or freewheel clutches specially adapted for cycles with hinged pawl co-operating with teeth, cogs, or the like
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
- Retarders (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
Abstract
The present invention provides a kind of Bicycle drive unit, which saves the space arranging gear, and achieves lightweight and densification.The driver element of the bicycle of the present invention includes: motor, has rotor (121) and is arranged in the stator (123) of radial outside of rotor (121)；And gear (140), it is possible to selecting multiple gear ratio, stator has notch (121a), and a part for gear (140) is configured at notch (121a).
Description
Technical field
The present invention relates to the driver element using motor output as auxiliary power and the electrically assisted bicycle with gear.
Background technology
As using the output of electro-motor (hereinafter referred to motor) as the electrically assisted bicycle of auxiliary power, there is the invention described in patent documentation 1.In the power unit of the electrically assisted bicycle of patent documentation 1, a part of otch of DC Brushless Motor is arranged out space, is provided with output transmission mechanism parts and the legpower testing agency etc. of such as crank axle, manpower driving system or electrical motor driven system within this space.
Prior art literature
Patent documentation 1: Japanese Unexamined Patent Publication 9-188286 publication.
In patent documentation 1 disclosed invention, when being arranged to the rotating speed changing trailing wheel relative to the gear of the ratio of the rotating speed of crank, such as need to arrange built-in variable speed device at rear-wheel hub, or multiple sprocket wheel and external variator are set at rear-wheel hub, it is necessary to arrange gear respectively with the unit including motor.It addition, in above-mentioned electrically assisted bicycle, it is desirable to output the having in the driver element of motor and carrying out speed change at electrically assisted bicycle of manpower driving system and electrical motor driven system.If adding gear in the unit include motor, then there is unit and become the possibility weighing or becoming big undesirably.
Summary of the invention
In view of above-mentioned problem, it is an object of the invention to provide a kind of driver element of bicycle including motor and gear and achieving lightweight and densification.
Driver element for solving the bicycle of above-mentioned problem is characterised by, including: motor, there is rotor and the stator of the radial outside being arranged in rotor；And gear, it is possible to selecting multiple gear ratio, stator has notch, and a part for gear is configured at notch.
Even if hereby it is achieved that including motor and gear also is able to realize the driver element of the bicycle of lightweight and densification.
And, rotor can have the hole that can configure crank axle.By configuration motor around crank axle, it is achieved that the driver element of the bicycle of lightweight and densification.
Additionally, notch can by axially being formed at stator otch on the whole at the rotating shaft of motor.Thereby, it is possible to increase the part that can be configured at notch of gear.
Additionally, notch can by being formed stator otch in the angular range of 120 ° around the rotation axis of motor.Thereby, it is possible to suppress the driving force of motor to reduce as far as possible, and cope with the configuration of the gear of all size.
It addition, gear can have planetary gears.Thus, there is the speed change that the bicycle of this driver element is capable of the rotation of crank axle.
It addition, the driver element of bicycle can also include crank axle.Further, crank axle can combine with the input portion of gear.Thereby, it is possible to the legpower of bicyclist is transferred to gear.
Additionally, the rotating shaft of the rotating shaft of crank axle and motor can be coaxially disposed.Thereby, it is possible to simplify the internal mechanism of motor, therefore, it is possible to realize further lightweight and the densification of the driver element of bicycle.
It addition, the driver element of bicycle can have: the first rotating shaft that crank axle and motor rotate；And the second rotating shaft that gear rotates.Thus, this driver element is formed by two axles, it is achieved that the lightweight of the driver element of bicycle and densification.
It addition, the driver element of bicycle can also include combining unit, the output of gear is added by this combining unit with the output of motor, and is connected to sprocket wheel in combining unit.Thereby, it is possible to utilize gear to select multiple gear ratios, therefore, it is possible to carry out the process auxiliary drive based on motor efficiently.And, it is possible to the output of combining unit is delivered to rear-wheel hub etc..
It addition, the output of motor can be transferred to combining unit via one-way clutch.Thereby, it is possible to prevent the revolving force of crank axle to be transferred to motor.
It addition, the driver element of bicycle can also have reducing gear, the output of motor is transferred to combining unit via reducing gear.Thereby, it is possible to be transferred to combining unit after the output of motor being slowed down, therefore, it is possible to realize making motor composition portion efficiently.
It addition, the driver element of bicycle can also have reducing gear, the output of motor is imported into reducing gear, and the output of reducing gear is transferred to combining unit via one-way clutch.Thus, can not only realize making motor composition portion efficiently, and the revolving force being prevented from combining unit is transferred to motor.
Furthermore it is possible to be arranged in a side in the rotation axis direction of motor for combining unit, the opposing party in the rotation axis direction of motor configures the link mechanism linking crank axle and gear.Thus, mechanism and the liftoff both sides being arranged in motor of composite part are linked, therefore, it is easy to obtain the weight balancing in the rotation axis direction of crank axle.
Furthermore it is possible to have planetary gears for gear, planetary gears has tooth rest, and tooth rest has planetary gear, and tooth rest is supported on combining unit.Thus, there is the speed change that the bicycle of this driver element is capable of the rotation of crank axle.
It addition, the rotating shaft of the rotating shaft of combining unit and crank axle can be coaxially disposed.Thereby, it is possible to make the bearing integrated of the rotating shaft of combining unit and the rotating shaft of crank axle, it is achieved that the further lightweight of the driver element of bicycle and densification.
It addition, the importation of gear and output part can rotate around the second rotating shaft.Thus, it is configured to baroque gear and motor and rotates around different rotating shafts, therefore easily assemble.
It addition, combining unit can have: the first joint portion combined with the output part of gear；And the second joint portion being combined with motor.Thus, the rotating torques of the rotating torques of crank axle and motor can be synthesized by this driver element.
Invention effect
According to the present invention, in including the driver element of bicycle of motor and gear, it is achieved that lightweight and densification.
Accompanying drawing explanation
Fig. 1 is the side view of the electrically assisted bicycle of the driver element of the first embodiment assembling the present invention.
Fig. 2 is the sectional view of the driver element of first embodiment of the present invention.
Fig. 3 is the side view of the motor observed of the cutting line III-III from Fig. 2 and variator.
Fig. 4 is the longitudinal section of the internal gear shifting hub of first embodiment of the present invention.
Fig. 5 is the axonometric chart of its axle.
Fig. 6 is the sectional elevation of the first one-way clutch.
Fig. 7 is the sectional elevation of the second one-way clutch.
Fig. 8 is the sectional elevation of the 3rd one-way clutch.
Fig. 9 is the exploded perspective view of switching mechanism.
Figure 10 is the front view of cam supporting parts.
Figure 11 is the half sectional view of cam supporting parts.
Figure 12 is second clutch mechanism is sectional elevation during connecting state.
Figure 13 is second clutch mechanism is sectional elevation during link releasing state.
What Figure 14 indicated that the first operation tube and the second operation tube can the sectional elevation of relative rotation range.
Figure 15 is the sectional view of the driver element of the variation of first embodiment of the present invention.
Description of reference numerals
1 driver element；14 output portions；32 planetary gears；102 crank axles；103 sprocket wheels；120 motors；121 stators；121a notch；123 rotors；125 reducing gears；131 torque compound components；132 one-way clutch；140 gears.
Detailed description of the invention
<the first embodiment>
Fig. 1 indicates that the right side view of an example of the electrically assisted bicycle of the driver element assembling the present invention.This electrically assisted bicycle will act on the legpower of pedal 100 through following path and is delivered to the hub body that can arrange rotatably around axletree 106 of rear wheel, and described path is crank arm 101 → crank axle, 102 → driver element 1 → front sprocket wheel 103 → chain 104 → rear sprocket wheel 105.In this process, motor output is assisted traveling as auxiliary power synthesis by this electrically assisted bicycle.Generally, utilize torque detection means to detect the torque acting on crank axle 102, when its detected value has exceeded setting value, start motor and produce the torque corresponding with legpower as auxiliary power.Torque detection means such as includes magnetostriction element and detection coil on crank axle 102, detects the torsion of crank axle 102.It is generally disposed at including the driver element 1 of motor of auxiliary near the linking part of rearward end of the bottom of the seat pipe of vehicle frame and the lower pipe of vehicle frame, and is fixed on vehicle frame by not shown bolt.The battery that motor drives configures along after-frame, lower pipe or seat pipe.
In the present invention, the output shaft of crank axle and motor is constituted coaxially, adds the axle of gear, two axles constitute driver element.Further, it is a feature of the present invention that there is notch in the stator of motor, this notch configures a part for gear.Below the 26S Proteasome Structure and Function of driver element 1 is illustrated.
Fig. 2 is the sectional view of the driver element of first embodiment of the present invention.As in figure 2 it is shown, in this driver element 1, insert in crank axle 102 in the through hole 111A of housing 111, and it is rotatably freely supported on housing 111 via bearing 112,113.Crank arm 101 can be installed removably at the two ends of crank axle 102.Crank arm 101 is arranged in the outside of housing 111.
<composition of auxiliary motor>
Motor (motor) 120 is configured to the rotating shaft coaxle of its rotating shaft and crank axle 102.The stator 121 of motor 120 is wound with excitation coil and is arranged on the concentric circular of crank axle 102, and is fixed on housing 111 by installation portion 122.Rotor 123 has the hole 123a that can configure crank axle 102.Hole 123a is along the through rotor 123 in rotation axis direction of rotor 123, and crank axle runs through and is inserted in the 123a of hole.Rotor 123 is rotatably freely supported on crank axle 102.Motor 120 is realized by DC Brushless Motor.Rotor 123 has: such as have the Magnet 123c of multiple magnetic pole in circumference；And keep the Magnet maintaining part 123b of Magnet.Rotor 123 is rotatably freely supported on crank axle 102 by the clutch shaft bearing 124a configured at spaced intervals along crank axle direction and the second bearing 124b.
The motor of present embodiment is the inner rotor type motor that rotor 123 is arranged to be surrounded from outside by stator 121.Wherein, as it is shown on figure 3, there is notch 121a in the part of stator 121.Being formed with multiple groove 121b in stator 121, the plurality of groove 121b is being arranged side by side in the circumference of rotating shaft.It is provided with coil 121c, thus constituting phase between each groove 121b.Stator 121 in present embodiment is 3 phase 9 grooves.Here, stator 121 can be 3 phase 12 grooves, it is also possible to is 3 phase 15 grooves, as long as 3 phases (3 × N) groove (N is positive integer).Notch 121a is by axially being formed at the otch on the whole of stator 121 at the rotating shaft of motor 120.Notch 121a is by being formed stator 121 otch in the angular range of α around the rotation axis of motor 120.α is preferably 120 °.
It addition, motor 120 is by the Driven by inverter eliminating diagram.Inverter is driven by not shown control portion, and control portion controls inverter according to legpower and speed.
<composition of reducing gear>
The rotation of rotor 123 is delivered to torque transmission member 130 by reducing gear 125.Fig. 2 is illustrated the planetary gears including central gear 126a and multiple planetary gear 126b as the one of reducing gear 125, but reducing gear 125 can also be formed by the multiple planetary gears being arranged side-by-side on crank axle direction.In the present embodiment, torque transmission member 130 is the tooth rest that planetary gear 126b remains the planetary gears that can rotate.The internal-gear 126c of planetary gears is fixed on housing 111.In this reducing gear 125, central gear 126a is supported to and can rotate relative to housing 111, and therefore, the gear ratio according to central gear 126a, planetary gear 126b and internal-gear 126c, by the rotational delay of motor 120 and be transferred to torque transmission member 130.
<linking the composition of mechanism>
Link mechanism and include the first gear 114 and the second gear 141.Link crank axle 102 and gear main body 140b.First gear 114 is arranged on the one end side of crank axle 102.First gear 114 is anchored on crank axle 102 and rotates integratedly with crank axle 102.First gear 114 such as can pass through sawtooth can be installed on crank axle 102 removably.Second gear 141 is the parts for torque is input to gear 140, engages with the first gear 114.Link mechanism and be arranged on torque compound component 131 and the opposite side of front sprocket wheel 103 across motor 120.
<composition of gear>
Gear 140 is made up of gear motor unit 140a and gear main body 140b.Gear motor unit 140a is by being assemblied in the instruction of the bicyclist at variable speed operation portion (not shown) place of handlebar, and makes the engagement body 88 of gear main body 140b described later rotate to predetermined phase place.As gear motor unit 140a, for instance the known motor unit that Japanese Patent No. 3529723 is disclosed can be used.Gear main body 140b is able to select the variator of multiple gear ratio.Gear main body 140b can select multiple speed change level in the present embodiment, and include rotary transfer machine and controlling organization, described rotary transfer machine has at least one planetary gear and central gear, and described controlling organization enables a part for described gear to rotate or can not rotate.Fig. 2 be enumerate three grades switching gears be that example is to illustrate the detailed description figure of gear main body 140b.
<composition of gear main body>
As shown in Figure 4, gear main body 140b includes axle 12, output portion 14, driving body (input portion) 16, rotary transfer machine 18 and switching mechanism 20.Axle 12 can be assemblied in housing 111 in non-rotatable mode.It addition, for the ease of illustrating, in the diagram, gear main body 140b towards with the gear main body 140b in Fig. 2 towards being heterochiral.Output portion 14 and driving body 16 are formed as tubular.Output portion 14 covers rotary transfer machine 18 and switching mechanism 20 together with driving body 16.The one end (in Fig. 4 left end) in output portion 14 is through there being bearing 22a to be rotatably freely supported on axle 12.Driving body 16 is rotatably freely supported on axle 12 via bearing 22b.The other end (in Fig. 4 right-hand member) in output portion 14 is rotatably freely supported on driving body 16 via bearing 22c.
Bearing 22a has: the inner ring 23a screwed with second external thread part 26 described later of axle 12；It is formed at the outer ring 23b of one end inner peripheral surface in output portion 14；And it is arranged in the steel ball 23c between inner ring 23a and outer ring 23b.Bearing 22b has: prevented the inner ring 23d rotated by the spline groove 27b described later of axle 12；It is formed at the outer ring 23e of one end inner peripheral surface of driving body 16；And it is arranged in the steel ball 23f between inner ring 23d and outer ring 23e.Bearing 22c has: be formed at the inner ring 23g of the outer peripheral face of driving body 16；It is formed at the outer ring 23h of the other end inner peripheral surface in output portion 14；And it is arranged in the steel ball 23i between inner ring 23g and outer ring 23h.
<composition of axle>
As it is shown in figure 5, axle 12 have at both ends for by nut 116(with reference to Fig. 2) be fixed to insert port 115(with reference to Fig. 2) and first external thread part 24a, 24b, this insert port 115 is formed at housing 111.Being formed with rotation prevention portion 25a, 25b at first external thread part 24a, 24b, this rotation prevention portion 25a, 25b are inserted into mouth 115 and prevent from rotating and being formed parallel to.Axially inner side at the first external thread part 24a is formed with the second external thread part 26 for assembling bearing 22a.Axially inner side at the first external thread part 24b is axially formed, with 180 degree of intervals, two splines groove 27a, 27b that width is different, and these two splines groove 27a, 27b are for preventing the component parts of bearing 22b and switching mechanism 20 from rotating.Axle 12 axial central part with 180 degree of intervals radially projecting be formed with the first jut 28 and the second jut 29, the first jut 28 plays a role as the one-way clutch of switching mechanism 20, and the second jut 29 plays a role as spline part.Axial central part at the second jut 29 is formed with location indentations 29a.
<composition in output portion>
Output portion 14 is rotatable around axle 12.As shown in Figure 4, output portion 14 is from one end (Fig. 4 left end) towards the expanding cartridge in the stepped ground of the other end (in Fig. 4 right-hand member).Peripheral part in output portion 14 is equipped with the 3rd gear 142 in not revolvable mode.Output portion 14 can rotate integratedly with the 3rd gear 142.
<composition of driving body>
Driving body 16 is the cartridge being rotatably assemblied in both between axle 12 and output portion 14.Driving body 16 is towards one end (in Fig. 4 right-hand member) stepped ground undergauge.It is equipped with the second gear 141 in the end with output portion 14 opposite side of driving body 16.Driving body 16 can rotate integratedly with the second gear 141.
<composition of rotary transfer machine>
Rotary transfer machine 18 has planetary gears 32, and the rotation of driving body 16 can be delivered to output portion 14 by after multiple (such as three) speed change level speed change by this planetary gears 32.Planetary gears 32 has: ring gear 34；First planet gear the 36, second planetary gear 38；The tooth rest 40 that first planet gear 36 and the second planetary gear 38 are rotatably supported；The first central gear 42 engaged with first planet gear 36；And the secondary sun wheel 44 engaged with the second planetary gear 38.Ring gear 34 is formed at the inner peripheral surface of another side (in Fig. 4 left side) of driving body 16.First planet gear 36 is at least one gear engaged with ring gear 34.Second planetary gear 38 can rotate integrally with first planet gear 36, is at least one (such as 30) gear of gear ratio first planet gear more than 36.In this embodiment, first planet gear 36 and the second planetary gear 38 are integrally formed, but can also split be formed.Three first planet gears 36 and the second planetary gear 38 respectively that configure at equal intervals in the circumferential are rotatably supported by tooth rest 40, and rotatable around axle 12.First central gear 42 be rotate around axle 12 and with first planet gear 36 meshed gears.Secondary sun wheel 44 be rotate around axle 12 and with the second planetary gear 38 meshed gears.Tooth rest 40 supports first planet gear 36 and the second planetary gear 38 by many (such as three) supporting axle 40a configured abreast with axle 12.
It addition, rotary transfer machine 18 also has the first one-way clutch 50 and the second one-way clutch 52.
First one-way clutch 50 has the first pawl support 54 of the tubular being rotatably assemblied in axle 12.First pawl support 54 can integrally rotatably link with tooth rest 40.First pawl support 54 has multiple (such as six) first assembling recess 54a of interval configuration in the circumferential at outer peripheral face, assembles recess 54a mesorelief the plurality of first and assembles first clutch pawl 55 described later freely.It addition, be adjacent at one end (in Fig. 4 right-hand member) with the first assembling recess 54a there is the link recess 54b that can integrally rotatably link with tooth rest 40.As shown in Figure 4, the locating snap ring 53 moving axially the outer peripheral face being assemblied in axle 12 of the first pawl support 54 is limited.As shown in Figure 6, the rotation shown in the arrow A of the direction of advance of the first pawl support 54 linked with tooth rest 40 is only transferred to output portion 14 by the first one-way clutch 50.
First one-way clutch 50 also has: rises and falls and is assemblied in multiple (such as six) first clutch pawl 55 of the first assembling recess 54a freely；And in the way of engaging, it is formed at the first ratchet 56 of the inner peripheral surface in output portion 14 with first clutch pawl 55.First clutch pawl 55 is erected attitude force by being assemblied in the first spring members 57 of the ring-type of the outer peripheral face of the first pawl support 54 towards what engage with the first ratchet 56.
As it is shown in fig. 7, the second one-way clutch 52 stop the first central gear 42 with the rotation shown in the arrow B of direction of advance opposite direction.As shown in Figure 4, the second one-way clutch 52 has the second pawl support 58 of the tubular not linked revolvably with axle 12.As it is shown in fig. 7, the inner circumferential at the second pawl support 58 has been protrudedly formed rotation prevention portion 58b towards radially inner side, this rotation prevention portion 58b has the engaging recessed part 58a that the second jut 29 with axle 12 engages.The alignment pin 59 that the movement in the direction of axle 12 of the second pawl support 58 is engaged with location indentations 29a limits.Alignment pin 59 is arranged in along the fixing hole 58c of the radial arrangement of the second pawl support 58.Thus, the second pawl support 58 links with axle 12 in the way of can not rotating and can not being axially moveable.
Second pawl support 58 has multiple (such as two) second assembling recess 58d of interval configuration in the circumferential at outer peripheral face, assembles in recess 58d the plurality of second and assembles second clutch pawl 60 described later in the way of rising and falling freely.It addition, the second pawl support 58 has the spring locking hole 58e of the other end 97b of the first torsionspring 97 described later for locking switching mechanism 20 at outer peripheral face.
Second one-way clutch 52 also has: is configured at the second assembling recess 58d and is assembled into multiple (such as two) the second clutch pawl 60 risen and fallen freely；And in the way of engaging, it is formed at the second ratchet 61 of the inner peripheral surface of the first central gear 42 with second clutch pawl 60.Second clutch pawl 60 is erected attitude force by being assemblied in the second spring members 62 of the ring-type of the outer peripheral face of the second pawl support 58 towards what engage with the second ratchet 61.
<composition of switching mechanism>
As shown in Figure 4, switching mechanism 20 has mobile parts 63, and this is moved parts 63 and can be moved by the rotation of the such as output shaft of the motor of gear motor unit 140a.It addition, switching mechanism 20 also has: first clutch mechanism 64, it is possible to corresponding to the movement of mobile parts 63, driving body 16 and tooth rest 40 at connecting state and are linked switching between releasing state；Second clutch mechanism 66, it is possible to corresponding to mobile parts 63 movement and by secondary sun wheel 44 can rotation status and can not switching between rotation status；And operating mechanism 70, it is possible to corresponding to the movement of mobile parts 63, first clutch mechanism 64 and second clutch mechanism 66 are switched over operation.
<compositions of mobile parts>
As shown in figures 4 and 9, move parts 63 to have: with the gear motor unit 140a engagement body 88(engaged with reference to Fig. 4)；Can with the first operation tube 90 of engagement body 88 linkage；And can with the second operation tube 92 of the first operation tube 90 linkage.
The state of the engagement body 88 inner ring 23d to be pressed on bearing 22b with the first external thread part 24b nut 160 screwed and gear motor unit 140a, is rotatably configured at the outer peripheral face of axle 12.The driving ring (not shown) of gear motor unit 140a is engaging in engagement body 88.Engagement body 88 is rotated by the action of gear motor unit 140a.Engagement body 88 is located in primary importance to the 3rd these three position, position by the action of gear motor unit 140a.Hereinafter, primary importance is recited as high speed position, the second position is recited as centre position, the 3rd position is recited as low-speed position.Such as, when indicating low speed action by being assemblied in the variable speed operation portion (not shown) of handlebar, engagement body 88 is configured to low-speed position, and when indicating high speed motion by variable speed operation portion (not shown), engagement body 88 is configured to high speed position.
First operation tube 90 is rotatably assemblied in the outer peripheral face of axle 12.As it is shown in figure 9, the first operation tube 90 at one end (in Fig. 9 right-hand member) has a pair engaging protrusion 90a of the arc-shaped engaging with engagement body 88 and axially extending.End at this engaging protrusion 90a is formed with engaging portion 90c, and this engaging portion 90c engages with engagement body 88 and circumferential lengths is slightly shorter.Engaging by this engaging portion 90c with the inner peripheral surface of engagement body 88 so that the rotation of the first operation tube 90 and engagement body 88 is positioned to certain position in above three position in linkage.Engaging protrusion 90a by cam part 80 described later by recess 80b engaging in engagement body 88.
The other end (in Fig. 9 left end) in the first operation tube 90 is formed with a pair first connecting piece 90b linked with the second operation tube 92.The circumferential lengths of the terminal part 90d of the first connecting piece 90b is shorter than the circumferential lengths of base end part.It addition, the outer peripheral face in the first operation tube 90 is formed with spring locking hole 90e, one end (in Fig. 9 right-hand member) 98a of the second torsionspring 98 described later is engaging in this spring locking hole 90e.
Second operation tube 92 at one end has a pair second connecting piece 92a of the arc-shaped engaged of the first connecting piece 90b with the first operation tube 90.The circumferential lengths of the terminal part 92b of the second connecting piece 92a is shorter than the circumferential lengths of base end part.As shown in figure 14, the first connecting piece 90b and the second connecting piece 92a is formed as relatively rotating predetermined angular β (such as 40 degree) left and right.It addition, the other end (in Fig. 9 left end) in the second operation tube 92 is integrally formed with a pair second control parts 85 for controlling second clutch mechanism 66.
<composition of first clutch mechanism>
As shown in Fig. 4, Fig. 8 and Fig. 9, first clutch mechanism 64 has: be arranged in the 3rd one-way clutch 72 between driving body 16 and tooth rest 40；And the 3rd one-way clutch 72 at connecting state and is linked the first control parts 73 controlled between releasing state.
Rotation shown in the arrow C of the direction of advance of driving body 16 is only transferred to tooth rest 40 by the 3rd one-way clutch 72.As shown in Figure 8, the 3rd one-way clutch 72 has: the 3rd clutch claw 74, and rising and falling to be assemblied in freely is formed in multiple (such as two) the 3rd assembling recess 16b of the inner peripheral surface of driving body 16；And the 3rd ratchet 75, in the way of engaging, it is formed at one end (in Fig. 4 right-hand member) outer peripheral face of tooth rest 40 with the 3rd clutch claw 74.3rd clutch claw 74 is erected attitude force by being assemblied in the 3rd spring members 76 of the ring-type of the inner peripheral surface of driving body 16 towards what engage with the 3rd ratchet 75.
As it is shown in figure 9, the first control parts 73 have: the cam part 80 linked with axle 12 in not revolvable mode；And the cam supporting parts 81 that can pivot.
Cam part 80 is the parts having bottom tube-like, has the locking projection 80a engaged of the spline groove 27a with axle 12 at inner peripheral surface.And inner peripheral surface have make the engaging protrusion 90a of the first operation tube 90 arc-shaped passed through by recess 80b.By recess 80b, there is the circumferential lengths that the circumferential lengths than engaging protrusion 90a is long, thus allowing the rotation of the preset range (such as substantially 40 degree) of the first operation tube 90.End face in the cylindrical portion of cam part 80 is formed and supports, with cam, the pair of angled cam 80c that parts 81 engage.Tilting cam 80c is made up of the inclined plane tilted in the circumferential.
As shown in Figure 10 and Figure 11, cam supporting parts 81 are the parts of ring-type, and within it side face is protrudedly formed the pair of cams fulcrum post 81a engaged with tilting cam 80c to radially inner side.Further, at one end face (Fig. 9 invading the interior side end face) is formed with multiple (such as eight) chain of command 81b, the plurality of chain of command 81b and what engage with the 3rd ratchet 75, the 3rd clutch claw 74 is erected switching between attitude and the lodging attitude deviated from from the 3rd ratchet 75.Chain of command 81b has in the circumferential configuration at spaced intervals and at circumference and the cam surface radially tilted.
As shown in Figure 4, the helical spring 83 that cam supporting parts 81 are configured between tooth rest 40 exerts a force to axially external (in Fig. 4 right side).When operating mechanism 70 rotatable parts described later 94 in Fig. 9 rotationally clockwise time, cam supporting pin 81a is engaged with the tilting cam 80c of cam part 80 by this rotation, thus cam supporting parts 81 overcome the active force of helical spring 83 to move to axially inner side (in Fig. 4 left side).By this to the movement of axially inner side, the 3rd clutch claw 74 is pressed towards lodging attitude by chain of command 81b from erecting attitude.Thus, the 3rd one-way clutch 72 becomes link releasing state.It addition, when rotatable parts 94 rotate to the counter clockwise direction in Fig. 9, the 3rd one-way clutch 72 returns connecting state.
<composition of second clutch mechanism>
As shown in Figure 12 and Figure 13, second clutch mechanism 66 has: be arranged in the 4th one-way clutch 84 between axle 12 and secondary sun wheel 44；And the 4th one-way clutch 84 at connecting state and is linked the second control parts 85 controlled between releasing state.
When the 4th one-way clutch 84 is in the connecting state shown in Figure 12, forbid the rotation shown in arrow D of the direction of advance of secondary sun wheel 44.4th one-way clutch 84 has: the 4th clutch claw 86, and rising and falling to be assemblied in freely is formed in multiple (such as two) the 4th assembling recess 44a of the inner peripheral surface of secondary sun wheel 44；And first jut 28, in the way of engaging, it is formed at the outer peripheral face of axle 12 with the 4th clutch claw 86.4th clutch claw 86 is erected attitude force by being assemblied in the 4th spring members 87 of the ring-type of the inner peripheral surface of secondary sun wheel 44 towards what engage with the first jut 28.
Second controls parts 85 is integrally formed a pair parts that cross section is arc-shaped in the second operation tube 92.Fig. 4 right flank of the second the first jut 28 controlling parts 85 and axle 12 closely configures.Second controls the parts 85 pivoting by the second operation tube 92 and releases at the coupling position shown in Figure 12 and the link shown in Figure 13 and rotate between position.When the second control parts 85 turn to link releasing position, the 4th clutch claw 86 is pressed to lodging attitude side, and the 4th one-way clutch 84 becomes link releasing state, thus secondary sun wheel 44 can forward direction rotation.
<composition of operating mechanism>
As shown in figures 4 and 9, operating mechanism 70 has the rotatable parts 94 rotated in linkage with the second operation tube 92 and the reset components 96 rotated in linkage with the second operation tube 92.It addition, operating mechanism 70 has the first torsionspring 97 and the second torsionspring 98.
Rotatable parts 94 are by metallic plate carries out discoideus parts that are stamping and that formed.Rotatable parts 94 are set for making the rotation of cam supporting parts 81 and engagement body 88 be correspondingly rotated.Rotatable parts 94 include: the substantially main part 94a of washer-shaped；And from peripheral part two lateral buckling 90 degree of main part 94a prominent a pair snap-latch piece 94b.Inner peripheral surface at main part 94a is formed: with the terminal part 90d of the first connector 90b of the first operation tube 90 the first engaging recessed part 94c engaged；And with the terminal part 92b of the second connecting piece 92a of the second operation tube 92 the second engaging recessed part 94d engaged.Middle body at snap-latch piece 94b is formed with holding tank 94e, and this holding tank 94e is axially moveable the cam supporting pin 81a of the parts 81 of clamp cam supporting freely.A snap-latch piece 94b is formed by the spring locking hole 94f locking for other end 98b of the second torsionspring 98.
Reset components 96 is by metallic plate carries out discoideus parts that are stamping and that formed.Reset components 96 is set for the active force of the first torsionspring 97 is delivered to the first operation tube 90 and the second operation tube 92, so that the first operation tube 90 and the second operation tube 92 rotate to the counter clockwise direction in Fig. 9.Reset components 96 has in inner circumferential side: with the terminal part 90d of the first connecting piece 90b of the first operation tube 90 the first engaging recessed part 96a engaged；And with the terminal part 92b of the second connecting piece 92a of the second operation tube 92 the second engaging recessed part 96b engaged.Further, it is formed spring locking hole 96c locking for one end (in Fig. 9 right-hand member) 97a of the first torsionspring 97 at the sidepiece of reset components 96.
First torsionspring 97 is such as torsion-coil spring, and the back-moving spring as the first operation tube 90 and the second operation tube 92 plays a role.That is, when gear motor unit 140a to position from high speed position towards intermediate position or to be positioned against low-speed position location from middling speed, the first operation tube 90 and the second operation tube 92 and engagement body 88 is made to rotate to the counter clockwise direction in Fig. 9.As it was previously stated, one end 97a of the first torsionspring 97 is engaging in reset components 96, and other end 97b is engaging in second pawl support 58 not revolvable relative to axle 12.
Second torsionspring 98 is such as torsion-coil spring, is used for making the first operation tube 90 and the second operation tube 92 link.Specifically, this second torsionspring 98 is arranged for following purpose: when the 3rd one-way clutch 72 or the 4th one-way clutch 82 can not switch over operation with power delivery status, makes the second operation tube 92 rotate after power delivery status releases.As it was previously stated, one end 98a of the second torsionspring 98 is engaging in the first operation tube 90, and the other end is engaging in rotatable parts 94.Therefore, the rotation of the first operation tube 90 is transferred to the second operation tube 92 via the second torsionspring 98 and rotatable parts 94.
<action of switching mechanism>
Below, the action of the switching mechanism 20 of the action based on gear motor unit 140a is illustrated.
When making engagement body 88 navigate to high speed position by the action of gear motor unit 140a, in first clutch mechanism 64, the first cam supporting parts 81 controlling parts 73 are configured to deviate from from the 3rd clutch claw 74 of the 3rd one-way clutch.Therefore, the 3rd one-way clutch becomes connecting state, and the rotation of driving body 16 is passed to tooth rest 40.Therefore, planetary gears 32 does not carry out action, and the rotation of driving body 16 is directly delivered to output portion 14 via tooth rest 40 and the first one-way clutch 50.Further, the rotation of final driving body 16 is passed to the 3rd gear 142.Should be delivered to, via tooth rest 40, the constant-speed transmission path that the path in output portion 14 is the function not using planetary gears 32 from driving body 16.
When making engagement body 88 navigate to centre position from high speed position by the action of gear motor unit 140a, engagement body 88 rotates, and the first operation tube 90 correspondingly rotates to the counter clockwise direction in Fig. 9.Thus, in first clutch mechanism 64, the cam supporting parts 81 of the first control parts 73 rotationally clockwise, move to the left side in Fig. 4 simultaneously, the 3rd clutch claw 74 of the 3rd one-way clutch 72 will be pressed into lodging attitude in Fig. 9.But, when bicyclist's Pedalling 100, the 3rd clutch claw 74 of the 3rd one-way clutch 72 becomes power transmission state, and therefore cam supporting parts 81 cannot press the 3rd clutch claw 74.Therefore, even if the first operation tube 90 rotates, rotatable parts 94 and the second operation tube 92 also do not rotate, and the second torsionspring 98 bends, and its power is accumulated.Then, when bicyclist stops Pedalling 100, rotatable parts 94 and the second operation tube 92 are rotated clockwise by the active force of the second torsionspring 98.Thus, first clutch mechanism 64 becomes link releasing state, and planetary gears 32 is by being arranged at the ring gear 34 of driving body 16 and action.
When being positioned at this centre position, second clutch mechanism 66 becomes the connecting state shown in Figure 12.Therefore, the counter-rotating of secondary sun wheel 44 is prevented from, when ring gear 34 forward direction rotates, secondary sun wheel 44 does not rotate, the speed reducing ratio rotation of driving body 16 determined with the engagement by the second planetary gear 38 and secondary sun wheel 44 is slowed down, and makes tooth rest 40 forward direction rotate.This rotation is transferred to output portion 14 via the first one-way clutch 50.Therefore, compared with the situation of high speed position, the rotating speed in output portion 14 reduces.It addition, when bicyclist's not Pedalling 100, rotatable parts 94 and the second operation tube 92 and the first operation tube 90 rotate in linkage.
Should make the path that tooth rest 40 slows down from the driving body 16 effect by the second planetary gear 38 and secondary sun wheel 44 be the deceleration bang path of the high-speed side two deceleration bang paths.
When making engagement body 88 from middling speed location positioning to low-speed position by the action of gear motor unit 140a, first clutch mechanism 64 is still for linking releasing state.Further, in second clutch mechanism 66, as shown in figure 13, second controls parts 85 first jut 28 with axle 12 in rotation direction and overlaps.Therefore, the 4th clutch claw 86 is no longer able to engage with the first jut 28, and second clutch mechanism 66 becomes link releasing state.Therefore, secondary sun wheel 44 can rotate to both direction, it is impossible to plays the function as central gear.As a result of which it is, the speed reducing ratio rotation of driving body 16 determined with the engagement by first planet gear 36 and the first central gear 42 is slowed down, and tooth rest 40 forward direction is made to rotate.Now, the number of teeth of the gear ratio secondary sun wheel 44 of the first central gear 42 is many, therefore, makes to deceleration further than centre position tooth rest 40 forward direction rotate.
Should make the path that tooth rest 40 slows down further from the driving body 16 effect by first planet gear 36 and the first central gear 42 be the deceleration bang path of the low speed side two deceleration bang paths.
On the other hand, when operating to high speed position from low-speed position when the action by gear motor unit 140a, active force by the first torsionspring 97, via reset components 96 make the second operation tube 92 in Fig. 9 rotationally clockwise, correspondingly, first operation tube 90 and rotatable parts 94 also rotate to the counter clockwise direction in Fig. 9, thus carrying out gear shifting operation to high speed position side.
<torque compound component>
Torque compound component 131 is arranged on the side, the other end of crank axle 102.It is formed as ring-type, has the second annulus radially extended along the first annulus of crank axle 102 extension and the end from the first annulus about crank axle 102.Second annulus is configured at the end by motor-side of the first annulus.The peripheral part of torque compound component 131 is made up of gear 131a.Gear 131 is formed at the peripheral part of the second annulus.Peripheral part and the 3rd gear 142 of torque compound component 131 engage.The inner peripheral portion of torque compound component 131 links via one-way clutch 132 and torque transmission member 130.Inner peripheral portion at the first annulus is formed with the clutch tank of one-way clutch 132.Torque compound component 131 is additionally provided with the rotation supporting portion 133 of the rotation of supporting torque transmission member 130.Rotation supporting portion 133 is arranged at the second annulus.Inner peripheral portion at torque compound component 131 is provided with bearing 113, and crank axle 102 is supported as rotating by torque compound component 131.Inner peripheral portion at the first annulus arranges bearing 113.Peripheral part at torque compound component 131 is provided with bearing 134, and torque compound component 131 is supported as rotating by housing 111.Peripheral part at the first annulus arranges bearing 134.Bearing 113 and one-way clutch 132 are closely arranged across the first annulus.So that sprocket wheel 103 can be provided with in the way of rotating with being integrally forming with torque compound component 131 on torque compound component 131.The end (end of the first annulus) of torque compound component 131 is prominent to outside from the hole 111A of housing 111.Such as by bolt, sprocket wheel 103 can be installed removably in the end of the first annulus of this torque compound component 131.
<action of driver element>
Next the action of this driver element is illustrated.The torque produced based on the legpower of bicyclist is so transmitted via gear: crank arm 101 → crank axle 102 → the first gear 114 → the second gear 141 → gear main body 140b → the 3rd gear 142 → torque compound component 131.On the other hand, so transmit from the output torque of motor: reducing gear 125 → torque transmission member, 130 → one-way clutch, 132 → torque compound component 131.The two torque is synthesized by torque compound component 131, and the torque after synthesis is delivered to sprocket wheel 103.Thus achieve the auxiliary based on motor.
<effect of the first embodiment>
Next the effect of present embodiment is illustrated.In the driver element of present embodiment, the stator of motor has notch, and a part for gear is arranged in notch, therefore, it is possible to realize the driver element of the bicycle of lightweight and densification.
It addition, as the input torque of gear, do not input the output torque of motor, therefore, even if gear is the gear including the planetary gears same with built-in variable speed mechanism, bicyclist also is able to carry out swimmingly the switching of level.Further, owing to utilizing gear can select multiple gear ratio, therefore, it is possible to carry out the process auxiliary drive based on motor efficiently.
Additionally, in the gear 140 of present embodiment, use in normally used auxiliary bike in the stage the most at a high speed that frequency ratio is higher, do not use the deceleration bang path of planetary gears 32.Therefore, the frequency using baroque planetary gears reduces, it is possible to the ruggedness maintaining gear 140 is good.
Additionally, in the present embodiment, the gear of the type pivoted for engagement body 88 and the first and second operation tube describes the present invention, but the invention is not restricted to this.For example, it is also possible to use and be there is the same gear of bell crank and the mechanism of the internal gear shifting hub of push rod that is axially moveable by bell crank, constitute the driver element of the present invention.Figure 15 represents the example employing such gear.Transmissions body 140b disclosed in Figure 15 is the internal gear shifting hub disclosed in No. 3428559 publications of Japanese Patent No., in this variator 140, replacing gear motor unit 140a to include speed change indicating mechanism 140c, this speed change indicating mechanism 140c comprises to receive and carries out the bell crank of action from the instruction in the variable speed operation portion (not shown) being assemblied in handlebar.It addition, transmissions body 140b comprises the push rod (not shown) being axially moveable by bell crank.
It addition, about gear 140, listing three-stage speed change mechanism is that example is illustrated, but gear 140 is not limited to aforementioned mechanism.Such as, gear 140 can also be Pyatyi, seven grades, eight grades, the mechanism of ten one-levels or progression in addition.These gears main body 140b such as can use the structure identical with the structure disclosed in No. 4564978 publications of Japanese Patent No., No. 3184230 publications of Japanese Patent No., No. 3654845 publications of Japanese Patent No. and No. 4705131 publications of Japanese Patent No..Also being able to obtain the effect identical with the first embodiment in these are constituted, this is apparent to those skilled in the art.It addition, the composition of above-mentioned gear is not limited to foregoing, as long as including at least a kind of gear in reducing gear and speed increasing mechanism.
In the explanation of embodiment above and variation, the content transmitted from the torque of the axial gear 140 of crank and carry out via gear to the torque of torque compound component 131 transmission from gear 140 is illustrated, but the transmission of these torques can also use band or chain to carry out.
It is made up of it addition, link mechanism the first gear 114 and the second gear 141, but it is also possible to use the gear of more than three to transmit driving force from crank axle 102 to gear 140.Alternatively, it is also possible to arrange multiple gear to transmit driving force between the output portion 14 and torque compound component 131 of gear.
Additionally, transmissions body 140b can be that buncher is to replace multiple-speed gear-box.And, if auxiliary motor 120 can be driven by low speed, then can also omit reducing gear 125.In this case, motor output is transferred directly to one-way clutch 132.
Speed change is performed manually by the above embodiment, but can also automatically carry out speed change.In this case, the velocity sensor of the speed of detection bicycle, the output according to velocity sensor of the control portion and the output from torque detection means being set, controlling gear motor unit 140a, thus carrying out the speed change of gear 140.
In the above-described embodiment, in order to guarantee the configuration space of variator 140 to greatest extent, it is preferable that α is more than 90 ° and below 120 °.
Claims (19)
1. a driver element for bicycle, including:
Motor, has rotor and the stator of the radial outside being arranged in described rotor；And
Gear, it is possible to select multiple gear ratio,
Described stator has notch,
A part for described gear is configured at described notch,
Described rotor has the hole that can configure crank axle.
2. the driver element of bicycle according to claim 1,
Described notch is by axially being formed at the axial otch on the whole of described stator at the rotating shaft of described motor.
3. the driver element of bicycle according to claim 1,
Described notch is by being formed described stator otch in the angular range of 120 ° around the rotation axis of described motor.
4. the driver element of bicycle according to claim 1,
Described gear has planetary gears.
5. the driver element of bicycle according to claim 1,
The driver element of described bicycle also includes described crank axle.
6. the driver element of bicycle according to claim 5,
The rotating shaft of described crank axle and the rotating shaft coaxle ground of described motor are arranged.
7. the driver element of bicycle according to claim 5,
Described crank axle combines with the input portion of described gear.
8. the driver element of bicycle according to claim 5,
The driver element of described bicycle has: the first rotating shaft that described crank axle and described motor rotate；And the second rotating shaft that described gear rotates.
9. the driver element of bicycle according to claim 1,
The driver element of described bicycle also includes combining unit, and the output of described gear is added by this combining unit with the output of described motor,
It is connected to sprocket wheel in described combining unit.
10. the driver element of bicycle according to claim 5,
The driver element of described bicycle also includes combining unit, and the output of described gear is added by this combining unit with the output of described motor,
It is connected to sprocket wheel in described combining unit.
11. the driver element of bicycle according to claim 8,
The driver element of described bicycle also includes combining unit, and the output of described gear is added by this combining unit with the output of described motor,
It is connected to sprocket wheel in described combining unit.
12. the driver element of the bicycle according to any one of claim 9 to 11,
The output of described motor is transferred to described combining unit via one-way clutch.
13. the driver element of the bicycle according to any one of claim 9 to 11,
The driver element of described bicycle also has reducing gear,
The output of described motor is transferred to described combining unit via reducing gear.
14. the driver element of the bicycle according to any one of claim 9 to 11,
The driver element of described bicycle also has reducing gear,
The output of described motor is imported into reducing gear,
The output of described reducing gear is transferred to described combining unit via one-way clutch.
15. the driver element of bicycle according to claim 10,
Described combining unit is arranged in the side in the rotation axis direction of described motor, and the opposite side in the rotation axis direction of described motor is configured with the link mechanism linking described crank axle and described gear.
16. the driver element of the bicycle according to any one of claim 9 to 11,
Described gear has planetary gears,
Described planetary gears has tooth rest, and this tooth rest has planetary gear,
Described tooth rest is supported on described combining unit.
17. the driver element of bicycle according to claim 10,
The rotating shaft coaxle ground of the rotating shaft of described combining unit and described crank axle is arranged.
18. the driver element of bicycle according to claim 11,
The importation of described gear and output part rotate around described second rotating shaft.
19. the driver element of bicycle according to claim 18,
Described combining unit has:
First joint portion of the described output part combination with described gear；And
The second joint portion being combined with described motor.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012-197181 | 2012-09-07 | ||
| JP2012197181A JP5442821B1 (en) | 2012-09-07 | 2012-09-07 | Bicycle drive unit |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103661761A CN103661761A (en) | 2014-03-26 |
| CN103661761B true CN103661761B (en) | 2016-07-06 |
Family
ID=50153401
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310401627.3A Active CN103661761B (en) | 2012-09-07 | 2013-09-06 | Bicycle drive unit |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP5442821B1 (en) |
| CN (1) | CN103661761B (en) |
| DE (1) | DE102013013881A1 (en) |
| TW (1) | TW201410539A (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6169531B2 (en) | 2014-05-21 | 2017-07-26 | 株式会社シマノ | Bicycle drive unit |
| JP6675110B2 (en) * | 2015-07-14 | 2020-04-01 | パナソニックＩｐマネジメント株式会社 | Drive unit and electric assist bicycle |
| DE102016217154A1 (en) * | 2016-09-08 | 2018-03-08 | Robert Bosch Gmbh | Drive arrangement and vehicle |
| EP3704013A1 (en) * | 2017-11-02 | 2020-09-09 | Wilfried Donner | Drive train comprising two separate shiftable gear mechanisms which are coupled by means of intermediate gear mechanisms |
| CN112072846A (en) * | 2020-08-21 | 2020-12-11 | 苏州莱士格车业有限公司 | Two-axis speed control center motor |
| WO2024114887A1 (en) * | 2022-11-28 | 2024-06-06 | Classified Cycling Bv | Bicycle transmission |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2179329Y (en) * | 1993-03-09 | 1994-10-12 | 吴子午 | Bicycle bottom bracket bearing speed variator |
| US6196347B1 (en) * | 1998-09-22 | 2001-03-06 | Industrial Technology Research Institute | Power transmission and pedal force sensing system for an electric bicycle |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03184230A (en) | 1989-12-14 | 1991-08-12 | Nec Corp | Impregnated cathode |
| JPH09188286A (en) * | 1996-01-10 | 1997-07-22 | Seiko Epson Corp | Electric bicycle |
| JP4056130B2 (en) * | 1997-12-26 | 2008-03-05 | 松下電器産業株式会社 | Driving assistance device in a battery-assisted bicycle |
| JP2003156077A (en) * | 2001-11-19 | 2003-05-30 | Moric Co Ltd | One-way clutch structure for electric driving device |
| JP5794928B2 (en) | 2011-03-08 | 2015-10-14 | 三菱電機株式会社 | Elevator abnormality diagnosis device |
-
2012
- 2012-09-07 JP JP2012197181A patent/JP5442821B1/en active Active
-
2013
- 2013-05-29 TW TW102118943A patent/TW201410539A/en unknown
- 2013-08-20 DE DE102013013881.7A patent/DE102013013881A1/en not_active Withdrawn
- 2013-09-06 CN CN201310401627.3A patent/CN103661761B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2179329Y (en) * | 1993-03-09 | 1994-10-12 | 吴子午 | Bicycle bottom bracket bearing speed variator |
| US6196347B1 (en) * | 1998-09-22 | 2001-03-06 | Industrial Technology Research Institute | Power transmission and pedal force sensing system for an electric bicycle |
Also Published As
| Publication number | Publication date |
|---|---|
| JP5442821B1 (en) | 2014-03-12 |
| TW201410539A (en) | 2014-03-16 |
| CN103661761A (en) | 2014-03-26 |
| DE102013013881A1 (en) | 2014-03-13 |
| TWI562935B (en) | 2016-12-21 |
| JP2014051193A (en) | 2014-03-20 |
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