CN204399435U - Bicycle use stepless change rear-guard axle - Google Patents
Bicycle use stepless change rear-guard axle Download PDFInfo
- Publication number
- CN204399435U CN204399435U CN201520059613.2U CN201520059613U CN204399435U CN 204399435 U CN204399435 U CN 204399435U CN 201520059613 U CN201520059613 U CN 201520059613U CN 204399435 U CN204399435 U CN 204399435U
- Authority
- CN
- China
- Prior art keywords
- wedge
- axle
- slotted disk
- level
- wedge claw
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Landscapes
- Structure Of Transmissions (AREA)
Abstract
The utility model relates to bicycle gear rear-guard axle, i.e. a kind of bicycle use stepless change rear-guard axle, and comprise fixed center axis, be arranged on the rear axle minor sprocket in fixed center axis and rear axle wheel hub, described rear axle wheel hub is positioned at rear axle minor sprocket side; Wherein: the side of described rear axle minor sprocket is disposed with first group of planetary dynamic gear train, wedge claw stepless speed changing mechanism, second group of planetary dynamic gear train and the 3rd group of planetary dynamic gear train, and described setting is all arranged in rear axle hub inner lumen.Due to described structure, this bicycle use stepless change rear-guard axle is possessed: extremely simple action can make speed change can be handling in the height put in place instantaneously; Can the high accelerating ability of shift in gradient continuously under various state; The high specialty comformability that moment of torsion is large, rotating speed is low, driving efficiency is high; Large speed ratio scope large be suitable for contain face and volume is little, lightweight, noiselessness, hermetically sealed lubrication can the many advantage such as practicality.
Description
Technical field
The utility model relates to bicycle gear rear-guard axle, especially a kind of high pulling torque, slow speed of revolution, the little quality of volume is little, the bicycle use stepless change rear-guard axle of the convenient and large field of application of high acceleration capability, high driving efficiency, large speed ratio scope, disposable accurately selected speed ratio point, speed change.
Background technology
The variable-speed drive being generally used for variable speed bicycle has internal speed-changing and outer speed change two kinds, and its mode of operation mainly relies on classification to shift gears and realizes the object of speed change.Although the development of process technology makes these devices accomplished to be close to ultimate attainment, the inherent limitation by its principle of work and gear shift mode affected, make they still exist on in-use performance many can not part fully up to expectations.
There is following technical matters in the bicycle gear driving device of prior art:
1, stepping speed change, with jaw clutch or the multistage engage a gear of raw mode of jumping chain, requires great effort consuming time, particularly large span speed change, disposablely rapidly can not reach optimum speed ratio state, also because not being uniform gradient ground speed change fast, make the acceleration capability of bicycle not good.
2, by the restriction of the mechanism of its gear shift mode, its classification gear number and ratio coverage are all subject to a definite limitation.
3. gear shifting operation is comparatively complicated, particularly external speed shifting mechanism, and user needs through necessarily training and could more skillfully grasping speed change skill; The speed change of large span must through repeatedly having shifted gears, and reaction is very slow, therefore can not adapt to the quick reaction requirement needed for complex road condition, the comformability fine setting in can not riding.
4. external speed shifting mechanism exposes completely, lubrication, dust-proof not good, use and deposit in process greatly affected by environment.
5. there is noise, as ratchet and trip stop noise etc.
6. restricted application is the situation of a kind of vehicle model substantially, and is difficult to be applied to other field.
In sum, the bicycle gear driving device Problems existing of prior art is: gearshift consuming time, the classification gear number of effort and ratio coverage is limited, acceleration capability is not good, affect by environment for use, have noise and restricted application.
Utility model content
An object of the present utility model is to provide a kind of high pulling torque, slow speed of revolution, the little quality of volume is little, the bicycle use stepless change rear-guard axle of the convenient and large field of application of high acceleration capability, high driving efficiency, large speed ratio scope, disposable accurately selected speed ratio point, speed change.
The technical scheme adopted for realizing the utility model above-mentioned purpose is: a kind of bicycle use stepless change rear-guard axle, comprises fixed center axis, is arranged on the rear axle minor sprocket in fixed center axis and rear axle wheel hub, and described rear axle wheel hub is positioned at rear axle minor sprocket side; It is characterized in that:
The side of described rear axle minor sprocket is disposed with first group of planetary dynamic gear train, wedge claw stepless speed changing mechanism, second group of planetary dynamic gear train and the 3rd group of planetary dynamic gear train, and described first group of planetary dynamic gear train, wedge claw stepless speed changing mechanism, second group of planetary dynamic gear train and the 3rd group of planetary dynamic gear train are arranged in rear axle hub inner lumen;
Described first group of planetary dynamic gear train comprises again sun gear I, this sun gear I is fixed on one end of the hollow rotating shaft of rear axle minor sprocket, what engage with sun gear I and inner gear I is planetary wheel I simultaneously, and the pivoted arm I being provided with planetary wheel I is connected with the power intake of wedge claw stepless speed changing mechanism;
Described second group of planetary dynamic gear train comprises again the sun gear II be fixed in fixed center axis, what engage with sun gear II and inner gear II is planetary wheel II simultaneously, described inner gear II is connected by the clutch end of adapter shaft with wedge claw stepless speed changing mechanism, and planetary wheel II is arranged on pivoted arm II;
Described 3rd group of planetary dynamic gear train comprises again the sun gear III be firmly connected mutually with rear axle wheel hub, what engage with sun gear III and inner gear III is planetary wheel III simultaneously, described planetary wheel III is arranged on pivoted arm III, the pivoted arm II of this pivoted arm III and second group of planetary dynamic gear train connects as one, and inner gear III is connected with the inner gear I of first group of planetary dynamic gear train by adapter shaft;
Described wedge claw stepless speed changing mechanism comprises the cubic shaft part that fixed center axis has, and is set with rectangular shaped slider frame at cubic shaft part place, and under External Force Acting, described rectangular shaped slider frame slides up and down at cubic shaft part place; Be set with square hole frame dish outside described rectangular shaped slider frame, under External Force Acting, described square hole frame dish horizontally slips outside rectangular shaped slider frame; In the fixed center axis of power intake, small eccentricity cover is set with at cubic shaft part, this small eccentricity cover is outer is set with the large eccentricity cover overlapping with small eccentricity and mate, under External Force Acting, small eccentricity is enclosed within large eccentricity cover and rotates around the axle center of fixed center axis, and described small eccentricity cover is integrally formed two offset concentric mechanism with large eccentricity cover; One end of described large eccentricity cover is tightly stuck in the outer of square hole frame dish, under External Force Acting, large eccentricity cover horizontally slips at cubic shaft part place with square hole frame dish one, under External Force Acting, described large eccentricity cover slides up and down at cubic shaft part place with the square hole frame dish linked with rectangular shaped slider frame, large eccentricity cover can not rotate, the axis of this large eccentricity cover can only make parallel vector shift, makes described rectangular shaped slider frame and square hole frame dish one form vector shift limiting mechanism at cubic shaft part place;
Described small eccentricity cover has extension hollow shaft section near power intake one side, this extension hollow shaft section is speed governing ingress pipe, this speed governing ingress pipe outer wall is connected by the one-level slotted disk of bearing with wedge claw one-level speed-changing mechanism, and described rectangular shaped slider frame is connected by the secondary stent of bearing with wedge claw two stage speed change mechanism on the shaft part of the fixed center axis of clutch end one side;
Wedge claw assembly in described wedge claw one-level speed-changing mechanism is identical with the wedge claw assembly structure in wedge claw two stage speed change mechanism;
Described wedge claw one-level speed-changing mechanism comprises again one-level support, this one-level support overlaps outer wall by the bearing being arranged in its endoporus with large eccentricity and is connected, the outer, chassis of described one-level support is provided with at least two group wedge claw assemblies, the chassis of described one-level support is arranged in the inner chamber of one-level slotted disk; The wedge claw assembly of described wedge claw one-level speed-changing mechanism also comprises connecting rod, one end of this connecting rod is hinged on by rack pin shaft on the chassis of one-level support, the other end of connecting rod is hinged on voussoir by wedge pawl pin axle, this voussoir swings around wedge pawl pin axle under external force, and cross section is the trapezoidal annular groove that the arc outer of trapezoidal voussoir is positioned on one-level slotted disk madial wall; The axle head at described wedge pawl pin axle diapire place in one-level slotted disk is provided with roller, the outer of this roller is tight against on the inner convex platform external cylindrical surface of one-level slotted disk, rotate around wedge pawl pin axle under described roller External Force Acting, this inner convex platform is positioned in the middle part of the diapire of one-level slotted disk, and the trapezoidal annular groove on inner convex platform and one-level slotted disk madial wall has same axle center; Be fixed with torque spring by spring pin in the fluting of described voussoir, one end of this torque spring is tight against on voussoir, and the other end of torque spring is tight against in the deep-slotted chip breaker of connecting rod waist; The predetermincd tension of described torque spring and the bearing force of roller are by the trapezoidal annular groove of the arc outer wedging of voussoir on one-level slotted disk madial wall;
Described wedge claw two stage speed change mechanism comprises again the secondary stent be arranged on the shaft part of the fixed center axis of clutch end by bearing, the outer, chassis of this secondary stent is provided with at least two group wedge claw assemblies, the chassis of described secondary stent is arranged in the inner chamber of secondary slotted disk, this secondary slotted disk and one-level support are fixed as one, be provided with bearing between the inwall of described secondary slotted disk and large eccentricity overlap, under External Force Acting, secondary slotted disk and one-level support integrated synchronous rotate; The wedge claw assembly of described wedge claw two stage speed change mechanism
Also comprise connecting rod, one end of this connecting rod is hinged on the chassis of secondary stent by rack pin shaft, the other end of connecting rod is hinged on voussoir by wedge pawl pin axle, this voussoir swings around wedge pawl pin axle under external force, and cross section is the trapezoidal annular groove that the arc outer of trapezoidal voussoir is positioned on secondary slotted disk madial wall; The axle head at described wedge pawl pin axle diapire place in secondary slotted disk is provided with roller, the outer of this roller is tight against on the inner convex platform external cylindrical surface of secondary slotted disk, rotate around wedge pawl pin axle under described roller External Force Acting, this inner convex platform is positioned in the middle part of the diapire of secondary slotted disk, and the trapezoidal annular groove on inner convex platform and secondary slotted disk madial wall has same axle center; Be fixed with torque spring by spring pin in the fluting of described voussoir, one end of this torque spring is tight against on voussoir, and the other end of torque spring is tight against in the deep-slotted chip breaker of connecting rod waist; The predetermincd tension of described torque spring and the bearing force of roller are by the trapezoidal annular groove of the arc outer wedging of voussoir on secondary slotted disk madial wall.
During use, the outer wall end of the speed governing ingress pipe of wedge claw stepless speed changing mechanism is fixed with a speed governing sheave, during use, this speed governing sheave is connected with the swing handle in bicycle handle bar by the speed governing steel cable of annular, rotate swing handle and drive speed governing steel cable, then drive speed trough to take turns forward and reverse rotation by speed governing steel cable.Rear axle minor sprocket is connected with the drive sprocket on bicycle middle shaft by chain, and the two ends of fixed center axis are separately fixed at vehicle frame chain stay rear end.
Due to said structure, this bicycle use stepless change rear-guard axle is made to have possessed the advantage of the convenient and large field of application of disposable accurately selected speed ratio point within the scope of high pulling torque, slow speed of revolution, little, the high acceleration capability of the little quality of volume, high driving efficiency, large speed ratio, speed change.
Accompanying drawing explanation
The nonlimiting examples that the utility model can be provided by accompanying drawing further illustrates.
Fig. 1 is the structural representation of the utility model bicycle use stepless change rear-guard axle.
Fig. 2 is the structural representation of the utility model wedge claw stepless speed changing mechanism.
The structural representation of Fig. 2 left apparent direction when Fig. 3 is two offset concentric mechanism A initial condition.
The structural representation of Fig. 2 left apparent direction when Fig. 4 is two offset concentric mechanism A eccentric state.
Fig. 5 is the structural representation of two offset concentric mechanism A initial condition in the left apparent direction of Fig. 2.
Fig. 6 is the structural representation of vector shift limiting mechanism B initial condition in the left apparent direction of Fig. 2.
Fig. 7 is the structural representation of two offset concentric mechanism A eccentric state in the left apparent direction of Fig. 2.
Fig. 8 is that in the left apparent direction of Fig. 2, vector shift limiting mechanism B makes the structural representation after in-plane displancement.
In figure: 1, fixed center axis; 2, small eccentricity cover; 3, large eccentricity cover; 4, rectangular shaped slider frame; 5, square hole frame dish; 6, one-level slotted disk; 7, one-level support; 8, secondary slotted disk; 9, secondary stent; 10, wedge claw assembly; 11, voussoir; 12, connecting rod; 13, roller; 14, wedge pawl pin axle; 15, spring pin; 16, torque spring; 17, rack pin shaft; 18, speed governing ingress pipe; 19, power intake; 20, clutch end; 21, first group of planetary dynamic gear train; 2101, sun gear I; 2102, planetary wheel I; 2103, inner gear I; 2104, pivoted arm I; 22, second group of planetary dynamic gear train; 2201, sun gear II; 2202, planetary wheel II; 2203, inner gear II; 2204, pivoted arm II; 23, the 3rd group of planetary dynamic gear train; 2301, sun gear III; 2302, planetary wheel III; 2303, inner gear III; 2304, pivoted arm III; 24, rear axle wheel hub; 25, chain; 26, rear axle minor sprocket; 27, speed governing steel cable; 28, speed governing sheave; 29, vehicle frame chain stay; 30, spoke; A, two offset concentric mechanism; B, vector shift limiting mechanism; C, wedge claw one-level speed-changing mechanism; D, wedge claw two stage speed change mechanism; E, wedge claw stepless speed changing mechanism.
Detailed description of the invention
Below in conjunction with drawings and Examples, the utility model is described in further detail:
See the bicycle use stepless change rear-guard axle in accompanying drawing 1 to 8, figure, comprise fixed center axis 1, be arranged on the rear axle minor sprocket 26 in fixed center axis 1 and rear axle wheel hub 24, described rear axle wheel hub 24 is positioned at rear axle minor sprocket 26 side; Wherein:
The side of described rear axle minor sprocket 26 is disposed with first group of planetary dynamic gear train 21, wedge claw stepless speed changing mechanism E, second group of planetary dynamic gear train 22 and the 3rd group of planetary dynamic gear train 23, and described first group of planetary dynamic gear train 21, wedge claw stepless speed changing mechanism E, second group of planetary dynamic gear train 22 and the 3rd group of planetary dynamic gear train 23 are arranged in rear axle wheel hub 24 inner chamber;
Described first group of planetary dynamic gear train 21 comprises again sun gear I 2101, this sun gear I 2101 is fixed on one end of the hollow rotating shaft of rear axle minor sprocket 26, what engage with sun gear I 2101 and inner gear I 2103 is planetary wheel I 2102 simultaneously, and the pivoted arm I 2104 being provided with planetary wheel I 2102 is connected with the power intake 19 of wedge claw stepless speed changing mechanism E;
Described second group of planetary dynamic gear train 22 comprises again the sun gear II 2201 be fixed in fixed center axis 1, what engage with sun gear II 2201 and inner gear II 2203 is planetary wheel II 2202 simultaneously, described inner gear II 2203 is connected by the clutch end 20 of adapter shaft with wedge claw stepless speed changing mechanism E, and planetary wheel II 2202 is arranged on pivoted arm II 2204;
Described 3rd group of planetary dynamic gear train 23 comprises again the sun gear III 2301 be firmly connected with rear axle wheel hub 24 phase, what engage with sun gear III 2301 and inner gear III 2303 is planetary wheel III 2302 simultaneously, described planetary wheel III 2302 is arranged on pivoted arm III 2304, the pivoted arm II 2204 of this pivoted arm III 2304 and second group of planetary dynamic gear train 22 connects as one, and inner gear III 2303 is connected by the inner gear I 2103 of adapter shaft with first group of planetary dynamic gear train 21;
Described wedge claw stepless speed changing mechanism E comprises the cubic shaft part that fixed center axis 1 has, and be set with rectangular shaped slider frame 4 at cubic shaft part place, under External Force Acting, described rectangular shaped slider frame 4 slides up and down at cubic shaft part place; Be set with square hole frame dish 5 outside described rectangular shaped slider frame 4, under External Force Acting, described square hole frame dish 5 horizontally slips outside rectangular shaped slider frame 4; In the fixed center axis 1 of power intake 19, small eccentricity cover 2 is set with at cubic shaft part, be set with outside this small eccentricity cover 2 and overlap 2 large eccentricities mated with small eccentricity and overlap 3, under External Force Acting, small eccentricity cover 2 rotates around the axle center of fixed center axis 1 in large eccentricity cover 3, and described small eccentricity cover 2 and large eccentricity overlap 3 and be integrally formed two offset concentric mechanism A; One end of described large eccentricity cover 3 is tightly stuck in the outer of square hole frame dish 5, under External Force Acting, large eccentricity cover 3 horizontally slips at cubic shaft part place with square hole frame dish 5 one, under External Force Acting, described large eccentricity cover 3 slides up and down at cubic shaft part place with the square hole frame dish 5 linked with rectangular shaped slider frame 4, large eccentricity cover 3 can not rotate, the axis of this large eccentricity cover 3 can only make parallel vector shift, makes described rectangular shaped slider frame 4 form vector shift limiting mechanism B with square hole frame dish 5 one at cubic shaft part place;
Described small eccentricity cover 2 has extension hollow shaft section near power intake 19 1 side, this extension hollow shaft section is speed governing ingress pipe 18, this speed governing ingress pipe 18 outer wall is connected by the one-level slotted disk 6 of bearing with wedge claw one-level speed-changing mechanism C, and described rectangular shaped slider frame 4 is connected by the secondary stent 9 of bearing with wedge claw two stage speed change mechanism D on the shaft part of the fixed center axis 1 of clutch end 20 1 side;
Wedge claw assembly 10 in described wedge claw one-level speed-changing mechanism C is identical with wedge claw assembly 10 structure in wedge claw two stage speed change mechanism D;
Described wedge claw one-level speed-changing mechanism C comprises again one-level support 7, this one-level support 7 overlaps 3 outer walls by the bearing being arranged in its endoporus with large eccentricity and is connected, the outer, chassis of described one-level support 7 is provided with at least two group wedge claw assemblies 10, the chassis of described one-level support 7 is arranged in the inner chamber of one-level slotted disk 6; The wedge claw assembly 10 of described wedge claw one-level speed-changing mechanism C also comprises connecting rod 12, one end of this connecting rod 12 is hinged on by rack pin shaft 17 on the chassis of one-level support 7, the other end of connecting rod 12 is hinged on voussoir 11 by wedge pawl pin axle 14, this voussoir 11 swings around wedge pawl pin axle 14 under external force, and cross section is the trapezoidal annular groove that the arc outer of trapezoidal voussoir 11 is positioned on one-level slotted disk 6 madial wall; The axle head at described wedge pawl pin axle 14 diapire place in one-level slotted disk 6 is provided with roller 13, the outer of this roller 13 is tight against on the inner convex platform external cylindrical surface of one-level slotted disk 6, rotate around wedge pawl pin axle 14 under described roller 13 External Force Acting, this inner convex platform is positioned in the middle part of the diapire of one-level slotted disk 6, and the trapezoidal annular groove on inner convex platform and one-level slotted disk 6 madial wall has same axle center; Be fixed with torque spring 16 by spring pin 15 in the fluting of described voussoir 11, one end of this torque spring 16 is tight against on voussoir 11, and the other end of torque spring 16 is tight against in the deep-slotted chip breaker of connecting rod 12 waist; The predetermincd tension of described torque spring 16 and the bearing force of roller 13 are by the trapezoidal annular groove of the arc outer wedging of voussoir 11 on one-level slotted disk 6 madial wall;
Described wedge claw two stage speed change mechanism D comprises again the secondary stent 9 be arranged on the shaft part of the fixed center axis 1 of clutch end 20 by bearing, the outer, chassis of this secondary stent 9 is provided with at least two group wedge claw assemblies 10, the chassis of described secondary stent 9 is arranged in the inner chamber of secondary slotted disk 8, this secondary slotted disk 8 is fixed as one with one-level support 7, the inwall of described secondary slotted disk 8 and large eccentricity are provided with bearing between overlapping 3, and under External Force Acting, secondary slotted disk 8 and one-level support 7 integrated synchronous rotate; The wedge claw assembly 10 of described wedge claw two stage speed change mechanism D
Also comprise connecting rod 12, one end of this connecting rod 12 is hinged on by rack pin shaft 17 on the chassis of secondary stent 9, the other end of connecting rod 12 is hinged on voussoir 11 by wedge pawl pin axle 14, this voussoir 11 swings around wedge pawl pin axle 14 under external force, and cross section is the trapezoidal annular groove that the arc outer of trapezoidal voussoir 11 is positioned on secondary slotted disk 8 madial wall; The axle head at described wedge pawl pin axle 14 diapire place in secondary slotted disk 8 is provided with roller 13, the outer of this roller 13 is tight against on the inner convex platform external cylindrical surface of secondary slotted disk 8, rotate around wedge pawl pin axle 14 under described roller 13 External Force Acting, this inner convex platform is positioned in the middle part of the diapire of secondary slotted disk 8, and the trapezoidal annular groove on inner convex platform and secondary slotted disk 8 madial wall has same axle center; Be fixed with torque spring 16 by spring pin 15 in the fluting of described voussoir 11, one end of this torque spring 16 is tight against on voussoir 11, and the other end of torque spring 16 is tight against in the deep-slotted chip breaker of connecting rod 12 waist; The predetermincd tension of described torque spring 16 and the bearing force of roller 13 are by the trapezoidal annular groove of the arc outer wedging of voussoir 11 on secondary slotted disk 8 madial wall.
For ease of assembling, in above-described embodiment, preferably: described power intake 19 is positioned on one-level slotted disk 6, this one-level slotted disk 6 is provided with the input installation portion installed for power input; Described clutch end 20 is positioned on secondary stent 9, this secondary stent 9 is provided with the output installation portion installed for power output member.
For ensureing stable drive, in above-described embodiment, preferably: the wedge claw assembly 10 in described wedge claw one-level speed-changing mechanism C is five groups with the wedge claw assembly 10 in wedge claw two stage speed change mechanism D.
For ease of the speed governing in bicycle running, in above-described embodiment, preferably: the outer wall end of described speed governing ingress pipe 18 is fixed with a speed governing sheave 28, during use, this speed governing sheave 28 is connected with the swing handle in bicycle handle bar by the speed governing steel cable 27 of annular.
Expanding ratio coverage for making whole rear-guard axle system, improving input speed, reducing input torque, and can realize in without ratchet device situation sliding, move backward and instead step on the functions such as plate, in above-described embodiment, preferably: the ratio of number of teeth of described sun gear I 2101, planetary wheel I 2102, inner gear I 2103 is 4:1:6.The ratio of number of teeth of described sun gear II 2201, planetary wheel II 2202, inner gear II 2203 is 8:7:22.The ratio of number of teeth of described sun gear III 2301, planetary wheel III 2302, inner gear III 2303 is 5:2:9.
In subsequent descriptions, the driving rotation direction of rear axle minor sprocket 26 is consistent with diagram rotation direction, and is confirmed as rotating forward or rotating forward, otherwise is then contrarotation or reversion; The axle center O of fixed center axis 1
1be confirmed as benchmark axle center, O
2when being eccentric drive, large eccentricity overlaps the axle center of 3 external cylindrical surfaces [outer wall], and and O
1parallel.
Whole bicycle use stepless change rear-guard axle in use, rear axle minor sprocket 26 does the rotating forward of drive actions, sun gear I 2101 and rear axle minor sprocket 26 rotating in same direction of first group of planetary dynamic gear train 21, motion is divided into two-way transmission by first group of planetary dynamic gear train 21, one tunnel positively passes to wedge claw stepless speed changing mechanism E through pivoted arm I 2104 and power intake 19, and an other road positively passes to the 3rd group of planetary dynamic gear train 23 through inner gear I 2103 and inner gear III 2303; Motion after the variable-speed processing of wedge claw stepless speed changing mechanism E lift-type is slowed down by second group of planetary dynamic gear train 22, motion after deceleration positively passes to rear axle wheel hub 24 by sun gear III 2301 after pivoted arm II 2204 and pivoted arm III 2,304 two of also positively passing to that the transmission of pivoted arm III 2304 and inner gear III 2303 comes by the 3rd group of planetary dynamic gear train the 23, three group of planetary dynamic gear train 23 move across differential synthesis.In this process, first group of planetary dynamic gear train 21 reality is Kinematic Decomposition differential gear train, by Kinematic Decomposition to wedge claw stepless speed changing mechanism E and the 3rd group of planetary dynamic gear train 23; Second group of planetary dynamic gear train 22 reality is deceleration train; 3rd group of planetary dynamic gear train 23 reality is by the differential gear train of motion synthesis.Because the efficiency of planetary gear transmission is generally higher than ordinary gear transmission, therefore the transmission process of described each group of dynamic gear train all belongs to efficient driving, up to 0.98.
The driving process of above-mentioned wedge claw stepless speed changing mechanism E is as follows:
Power intake 19 drives first-stage tank dish 6 to rotate forward with the motion that forward inputs, one-level slotted disk 6 promotes one-level support 7 by wedge claw assembly 10 forward in wedge claw one-level speed-changing mechanism C, rotate forward with the secondary slotted disk 8 of one-level support 7 one, secondary slotted disk 8 promotes secondary stent 9 by the wedge claw assembly 10 in wedge claw two stage speed change mechanism D and rotates forward, and secondary stent 9 is connected the forward realizing moving and exports with load.
During initial condition, small eccentricity cover 2 and large eccentricity overlaps 3 and assemble large eccentricity in the two offset concentric mechanism A formed afterwards and overlap the outer wall axle center of 3 and the axis coinciding of fixed center axis 1, small eccentricity cover 2 can only rotate forward under vector shift limiting mechanism B restriction, large eccentricity cover 3 is in end position, and can not rotate, can only upwards and to the right move integrally.Now, the slotted disk [one-level slotted disk 6 and secondary slotted disk 8] that wedge claw one-level speed-changing mechanism C is corresponding with wedge claw two stage speed change mechanism D and support [one-level support 7 and secondary stent 9] can only along the axle center O of fixed center axis 1
1rotate.In this process, the transmitting ratio of described wedge claw one-level speed-changing mechanism C and described wedge claw two stage speed change mechanism D is 1:1, specifically, in [wedge claw assembly in described wedge claw one-level speed-changing mechanism C 10 is all explained with the wedge claw assembly 10 in wedge claw two stage speed change mechanism D based on five groups] described wedge claw one-level speed-changing mechanism C the voussoir 11 of all wedge claw assemblies 10 all with the keystone ring slot wedge on one-level slotted disk 6 madial wall tightly thus drive one-level support 7, namely one-level slotted disk 6 promotes with the angle that pushes away of 2 π/5 corner that one-level support 7 turns over 2 π/5, this one-level support 7 directly drives secondary slotted disk 8, in described wedge claw two stage speed change mechanism D, the voussoir 11 of all wedge claw assemblies 10 is all tight with the keystone ring slot wedge on secondary slotted disk 8 madial wall thus drives secondary stent 9, and secondary slotted disk 8 pushes away also with 2 π/5 corner that angle promotion secondary stent 9 turns over 2 π/5.
When small eccentricity cover 2 rotates forward end position, namely under the restriction of vector shift limiting mechanism B, small eccentricity cover 2 can not again according to when rotating forward, and large eccentricity cover 3 is under the double action of two offset concentric mechanism A and vector shift limiting mechanism B, and the outer wall axle center of this large eccentricity cover 3 will from O
1move in parallel gradually to O
2now, in wedge claw one-level speed-changing mechanism C, one-level support 7 overlap 3 one movements with the pivot center of secondary slotted disk 8 in wedge claw two stage speed change mechanism D with large eccentricity, in wedge claw one-level speed-changing mechanism C in one-level support 7 and wedge claw two stage speed change mechanism D the pivot center of secondary slotted disk 8 also from O
1move to O gradually
2one-level slotted disk 6 in whole process in wedge claw one-level speed-changing mechanism C and the secondary slotted disk 8 between one-level support 7, in wedge claw two stage speed change mechanism D and between secondary stent 9, small eccentricity cover 2 rotation under realize stepless and accurately degree of eccentricity change, this degree of eccentricity variation range is at O
1with O
2between change in displacement.In this process, one-level slotted disk 6 in described wedge claw one-level speed-changing mechanism C is in eccentric state gradually with one-level support 7, one group of wedge claw assembly 10 in five groups of wedge claw assemblies 10 is promoted by one-level slotted disk 6 because of the wedge action driven, now one-level slotted disk 6 pushes away angle driving one-level support 7 with minimum effect and turns over a unit rotation, this corner is greater than and pushes away angle, be close to all the other wedge claw assemblies 10 of the front and back of described one group of wedge claw assembly 10, when turning over a unit rotation under the drive of driven one-level support 7, voussoir 11 on all the other wedge claw assemblies 10 will with O on one-level slotted disk 6
1the above-mentioned angle pushing away angle is greater than for axle center turns over one, namely the trapezoidal annular groove that the voussoir 11 on all the other wedge claw assemblies 10 can depart from one-level slotted disk 6 madial wall around wedge pawl pin axle 14 inverted wobbles, voussoir 11 namely on all the other wedge claw assemblies 10 is no longer tight with the keystone ring slot wedge on one-level slotted disk 6 madial wall, and these wedge claw assemblies 10 will be in free state and not participate in driving one-level support 7, when foregoing one group of wedge claw assembly 10 completes after an effect pushes away angle, all the other follow-up and next wedge claw assemblies 10 are understood in turn and are taken over the former continuation effect very reposefully, and this taking over is seamless continuous, thus make stable drive and successively, transmission is now carried out in raising speed mode, as shown in Figure 3, [only have the position relationship of one-level slotted disk 6 in the wedge claw one-level speed-changing mechanism C in figure, but due to its parts and drive connection all identical with wedge claw two stage speed change mechanism D, therefore can refer to explanation.] one-level slotted disk 6 pushes away angle with the effect being less than 2 π/5 and promotes the unit rotation that one-level support 7 has turned over 2 π/5, and degree of eccentricity is larger, and raising speed compares larger, and with the meticulous adjustment of degree of eccentricity, this transmission can be made to obtain can the stepless shift function of accurate speed governing, in like manner, also eccentric state is in gradually between the secondary slotted disk 8 of described wedge claw two stage speed change mechanism D and secondary stent 9, one group of wedge claw assembly 10 in five groups of wedge claw assemblies 10 is promoted by secondary slotted disk 8 because of wedge action, now secondary slotted disk 8 pushes away angle driving secondary stent 9 with minimum effect and turns over a unit rotation, this corner is greater than and pushes away angle, be close to all the other wedge claw assemblies 10 of the front and back of described one group of wedge claw assembly 10, when turning over a unit rotation under driven secondary stent 9 drives, voussoir 11 on all the other wedge claw assemblies 10 will with O on secondary slotted disk 8
2the above-mentioned angle pushing away angle is greater than for axle center turns over one, namely the trapezoidal annular groove that the voussoir 11 on all the other wedge claw assemblies 10 can depart from secondary slotted disk 8 madial wall around wedge pawl pin axle 14 inverted wobbles, voussoir 11 namely on all the other wedge claw assemblies 10 is no longer tight with the keystone ring slot wedge on secondary slotted disk 8 madial wall, and these wedge claw assemblies 10 will be in free state and not participate in driving secondary stent 9, when one group of wedge claw assembly 10 noted earlier completes after an effect pushes away angle, all the other follow-up and next wedge claw assemblies 10 are understood in turn and are taken over the former continuation effect very reposefully, and this taking over is seamless continuous, thus make stable drive and successively, transmission is now carried out in raising speed mode, as shown in Figure 3, secondary slotted disk 8 pushes away angle with the effect being less than 2 π/5 and promotes the unit rotation that secondary stent 9 has turned over 2 π/5, and degree of eccentricity is larger, and raising speed is than larger, with the meticulous adjustment of degree of eccentricity, this transmission can be made to obtain can the stepless shift function of accurate speed governing.In described wedge claw one-level speed-changing mechanism C, one-level support 7 and the pivot center of secondary slotted disk 8 in wedge claw two stage speed change mechanism D are from O
1move to O gradually
2, be a raising speed than the process strengthened gradually, certainly in use, the maximum raising speed of power intake 19 and clutch end 20 is than being generally no more than 1:1.44.
In above-mentioned working process, voussoir 11 angle of wedge departed from the direction of action of one-level slotted disk 6 in described wedge claw one-level speed-changing mechanism C be bigger than they advance time direction of action on the effect angle of wedge, and the Self-locking angle be bigger than between them, when part rigidity is enough, the action of its clutch can't produce mechanical loss, and wedge claw two stage speed change mechanism D is identical with the effect stating wedge claw one-level speed-changing mechanism C; Although what the transmission of transmission process medium power relied on is friction moment, relatively remain static between friction pair now, also with regard to saying without loss due to friction.Therefore, this type of drive is a kind of transmission that make use of the pure rigidity of friction force, and it all has very high driving efficiency in full ratio coverage.Under normal circumstances, its efficiency is higher than gear transmission, and general driving efficiency can up to 0.99.
The advantage of above-mentioned wedge claw stepless speed changing mechanism is as follows:
Reduce useless power consumption, improve function driving efficiency, reduce quality, reduce volume and reduce noise, also there is the function of one-way clutch simultaneously.
The specific works process that above-mentioned bicycle use stepless change rear-guard axle is applied in bicycle is:
Rotate hand and positive and negative rotation is driven speed governing steel cable 27, cause and regulate small eccentricity cover 2 to rotate, the rotation of small eccentricity cover 2 produces speed-ratio regulation to wedge claw stepless speed changing mechanism E, by realizing the speed-ratio regulation to whole rear-guard axle system to the speed-ratio regulation of wedge claw stepless speed changing mechanism E, and the stable of speed governing steel cable 27 relies on additional minimal friction thereon to come perfect.This structure can with the automatic adaptive pattern of maximum output torque and minimum speed and performance, and this pattern makes first group of planetary dynamic gear train 21 at any driving condition, and it can become a fixed pattern to the ratio relation of resolution of velocity and be fixed.After second group of planetary dynamic gear train 22 and the 3rd group of planetary dynamic gear train 23 are combined with wedge claw stepless speed changing mechanism E, what the raising speed stepless shift mode of wedge claw stepless speed changing mechanism E can be made to become bicycle use stepless change rear-guard axle rises deceleration stepless shift mode, and [when the stepless change speed ratio of wedge claw stepless speed changing mechanism E is 1:1 to 1:1.42, ratio coverage is 1.42 can to obtain a ratio coverage more much bigger than wedge claw stepless speed changing mechanism E; The stepless change speed ratio of corresponding bicycle use stepless change rear-guard axle is 1:0.253 to 1:1.116, and ratio coverage is 4.41; ], this also makes the input speed of whole bicycle stepless change rear-guard axle can improve and reduce input torque, thus reduces total quality and the volume of bicycle use stepless change rear-guard axle; Its large ratio coverage contains the requirement of the bicycle of various ratio coverage substantially, expands Applicable scope.
Bicycle drives route: the hinge wheel on bicycle middle shaft → planetary dynamic gear train 21 of chain 25 → rear axle minor sprocket 26 → the first groups, moves and punishes into two-way at first group of planetary dynamic gear train 21;
Wherein a road is the sun gear I 2101 → inner gear I 2102 → inner gear III 2303 in first group of planetary dynamic gear train 21;
An other road is inner gear II 2203 → pivoted arm II 2204 → pivoted arm III 2304 of the planetary dynamic gear train 22 of clutch end 20 → the second groups of secondary stent 9 → wedge claw stepless speed changing mechanism E of wedge claw assembly 10 → wedge claw two stage speed change mechanism D of secondary slotted disk 8 → wedge claw two stage speed change mechanism D of one-level support 7 → wedge claw two stage speed change mechanism D of wedge claw assembly 10 → wedge claw one-level speed-changing mechanism C of one-level slotted disk 6 → wedge claw one-level speed-changing mechanism C of power intake 19 → wedge claw one-level speed-changing mechanism C of sun gear I 2101 → pivoted arm I 2104 → wedge claw stepless speed changing mechanism E in first group of planetary dynamic gear train 21;
Two-way motion is derived by sun gear III 2301 after the 3rd group of planetary dynamic gear train 23 place synthesizes a road motion, and sun gear III 2301 → rear axle wheel hub 24 → spoke 30 → trailing wheel wheel rim, completes driving.[in driving process, mentioning that part rotation direction is all rotate forward]
Sliding: trailing wheel rotating forward → rear axle wheel hub 24 rotates forward → the secondary stent 9 forward idle running of sun gear III 2301 rotating forward → pivoted arm III 2304 rotating forward → pivoted arm II 2204 rotating forward → inner gear II 2202 rotating forward → wedge claw stepless speed changing mechanism E].
Reversing: trailing wheel reversion → rear axle wheel hub 24 reverses → sun gear III 2301 reversion → inner gear III 2302 rotating forward → inner gear I 2102 rotating forward → sun gear I 2101 reversion → rear axle minor sprocket 26 reverses → bicycle middle shaft on hinge wheel and pedal oppositely dally.
Instead step on plate: the hinge wheel reversion → rear axle minor sprocket 26 on bicycle middle shaft reverses → and the one-level slotted disk 6 of sun gear I 2101 reversion → pivoted arm I 2104 reversion → wedge claw stepless speed changing mechanism E oppositely dallies.
The advantage that the utility model has due to described structure is as follows:
1, due to its distinctive control mode, only once need twist the rotatable hand handle on handlebar, just can obtain the speed ratio gear of any the best; In driving is advanced, can also be uniform gradient ground continuous speed adjustment fast, make bicycle obtain splendid acceleration capability.
2, due to the transmission principle of its uniqueness, device can be made to obtain very large ratio coverage.
3, variable speed operation is very simple, and user can grasp without the need to any training.Even if very the gear shifting operation of large span also in completing instantaneously, more can adapt to the rapid reaction required for complex road condition and the adaptation of the fine setting in riding.
4, important parts can all be sealed in rear axle wheel hub, high lubricating effect, and parts are loss not easily, once refuel and can use for a long time, substantially can not be subject to environmental influence.
5, the utility model is without ratchet device, and without jaw clutch and jump chain gear shift action, therefore basic noiselessness, shakes minimum, is a peace and quiet and pulsation-free transmission device.
6, volume weight is little, takes up room very little; Applicable scope is very large, and the product of a model can contain the operating needs of various bicycle substantially; Repacking upgrading can be carried out to ordinary bicycle easily, directly can be processed into a part for the board-like trailing wheel of bicycle, automatic speed changing version can be upgraded to again, also can be applied to other non-maneuver transmission field easily.
Obviously, all embodiments of foregoing description are a part of embodiments of the present utility model, instead of whole embodiments.Based on embodiment of the present utility model, those of ordinary skill in the art are not making other embodiments all obtained under creative work prerequisite, all belong to the category of the utility model protection.
In sum, the utility model, due to said structure, makes this bicycle use stepless change rear-guard axle possess the advantage of the convenient and large field of application of disposable accurately selected speed ratio point within the scope of high pulling torque, slow speed of revolution, little, the high acceleration capability of the little quality of volume, high driving efficiency, large speed ratio, speed change.
Claims (7)
1. a bicycle use stepless change rear-guard axle, comprises fixed center axis (1), is arranged on the rear axle minor sprocket (26) in fixed center axis (1) and rear axle wheel hub (24), and described rear axle wheel hub (24) is positioned at rear axle minor sprocket (26) side; It is characterized in that:
The side of described rear axle minor sprocket (26) is disposed with first group of planetary dynamic gear train (21), wedge claw stepless speed changing mechanism (E), second group of planetary dynamic gear train (22) and the 3rd group of planetary dynamic gear train (23), and described first group of planetary dynamic gear train (21), wedge claw stepless speed changing mechanism (E), second group of planetary dynamic gear train (22) and the 3rd group of planetary dynamic gear train (23) are arranged in rear axle wheel hub (24) inner chamber;
Described first group of planetary dynamic gear train (21) comprises again sun gear I (2101), this sun gear I (2101) is fixed on one end of the hollow rotating shaft of rear axle minor sprocket (26), what engage with sun gear I (2101) and inner gear I (2103) is planetary wheel I (2102) simultaneously, and the power intake (19) of the pivoted arm I (2104) and wedge claw stepless speed changing mechanism (E) that are provided with planetary wheel I (2102) is connected;
Described second group of planetary dynamic gear train (22) comprises again the sun gear II (2201) be fixed in fixed center axis (1), what engage with sun gear II (2201) and inner gear II (2203) is planetary wheel II (2202) simultaneously, described inner gear II (2203) is connected with the clutch end (20) of wedge claw stepless speed changing mechanism (E) by adapter shaft, and planetary wheel II (2202) is arranged on pivoted arm II (2204);
Described 3rd group of planetary dynamic gear train (23) comprises again the sun gear III (2301) be firmly connected mutually with rear axle wheel hub (24), what engage with sun gear III (2301) and inner gear III (2303) is planetary wheel III (2302) simultaneously, described planetary wheel III (2302) is arranged on pivoted arm III (2304), this pivoted arm III (2304) connects as one with the pivoted arm II (2204) of second group of planetary dynamic gear train (22), inner gear III (2303) is connected with the inner gear I (2103) of first group of planetary dynamic gear train (21) by adapter shaft,
Described wedge claw stepless speed changing mechanism (E) comprises the cubic shaft part that fixed center axis (1) has, and is set with rectangular shaped slider frame (4) at cubic shaft part place, and under External Force Acting, described rectangular shaped slider frame (4) slides up and down at cubic shaft part place; Be set with square hole frame dish (5) outside described rectangular shaped slider frame (4), under External Force Acting, described square hole frame dish (5) horizontally slips outside rectangular shaped slider frame (4); In the fixed center axis (1) of power intake (19), small eccentricity cover (2) is set with at cubic shaft part, the large eccentricity cover (3) mated with small eccentricity cover (2) is set with outside this small eccentricity cover (2), under External Force Acting, small eccentricity cover (2) rotates around the axle center of fixed center axis (1) in large eccentricity cover (3), and described small eccentricity cover (2) and large eccentricity cover (3) are integrally formed two offset concentric mechanism (A); One end of described large eccentricity cover (3) is tightly stuck in the outer of square hole frame dish (5), under External Force Acting, large eccentricity cover (3) horizontally slips at cubic shaft part place with square hole frame dish (5) one, under External Force Acting, described large eccentricity cover (3) slides up and down at cubic shaft part place with the square hole frame dish (5) linked with rectangular shaped slider frame (4), large eccentricity cover (3) can not rotate, the axis of this large eccentricity cover (3) can only make parallel vector shift, makes described rectangular shaped slider frame (4) form vector shift limiting mechanism (B) with square hole frame dish (5) one at cubic shaft part place;
Described small eccentricity cover (2) has extension hollow shaft section near power intake (19) side, this extension hollow shaft section is speed governing ingress pipe (18), this speed governing ingress pipe (18) outer wall is connected with the one-level slotted disk (6) of wedge claw one-level speed-changing mechanism (C) by bearing, and described rectangular shaped slider frame (4) is connected with the secondary stent (9) of wedge claw two stage speed change mechanism (D) by bearing on the shaft part of the fixed center axis (1) of clutch end (20) side;
Wedge claw assembly (10) in described wedge claw one-level speed-changing mechanism (C) is identical with wedge claw assembly (10) structure in wedge claw two stage speed change mechanism (D);
Described wedge claw one-level speed-changing mechanism (C) comprises again one-level support (7), this one-level support (7) is connected with large eccentricity cover (3) outer wall by the bearing being arranged in its endoporus, the outer, chassis of described one-level support (7) is provided with at least two group wedge claw assemblies (10), the chassis of described one-level support (7) is arranged in the inner chamber of one-level slotted disk (6); The wedge claw assembly (10) of described wedge claw one-level speed-changing mechanism (C) also comprises connecting rod (12), one end of this connecting rod (12) is hinged on the chassis of one-level support (7) by rack pin shaft (17), the other end of connecting rod (12) is hinged on voussoir (11) by wedge pawl pin axle (14), this voussoir (11) swings around wedge pawl pin axle (14) under external force, and cross section is the trapezoidal annular groove that the arc outer of trapezoidal voussoir (11) is positioned on one-level slotted disk (6) madial wall; Described wedge pawl pin axle (14) is provided with roller (13) on the axle head at the interior diapire place of one-level slotted disk (6), the outer of this roller (13) is tight against on the inner convex platform external cylindrical surface of one-level slotted disk (6), rotate around wedge pawl pin axle (14) under described roller (13) External Force Acting, this inner convex platform is positioned in the middle part of the diapire of one-level slotted disk (6), and the trapezoidal annular groove on inner convex platform and one-level slotted disk (6) madial wall has same axle center; Be fixed with torque spring (16) by spring pin (15) in the fluting of described voussoir (11), one end of this torque spring (16) is tight against on voussoir (11), and the other end of torque spring (16) is tight against in the deep-slotted chip breaker of connecting rod (12) waist; The predetermincd tension of described torque spring (16) and the bearing force of roller (13) are by the trapezoidal annular groove of the arc outer wedging of voussoir (11) on one-level slotted disk (6) madial wall;
Described wedge claw two stage speed change mechanism (D) comprises again the secondary stent (9) be arranged on the shaft part of the fixed center axis (1) of clutch end (20) by bearing, the outer, chassis of this secondary stent (9) is provided with at least two group wedge claw assemblies (10), the chassis of described secondary stent (9) is arranged in the inner chamber of secondary slotted disk (8), this secondary slotted disk (8) and one-level support (7) are fixed as one, bearing is provided with between the inwall of described secondary slotted disk (8) and large eccentricity cover (3), under External Force Acting, secondary slotted disk (8) and one-level support (7) integrated synchronous rotate, the wedge claw assembly (10) of described wedge claw two stage speed change mechanism (D)
Also comprise connecting rod (12), one end of this connecting rod (12) is hinged on the chassis of secondary stent (9) by rack pin shaft (17), the other end of connecting rod (12) is hinged on voussoir (11) by wedge pawl pin axle (14), this voussoir (11) swings around wedge pawl pin axle (14) under external force, and cross section is the trapezoidal annular groove that the arc outer of trapezoidal voussoir (11) is positioned on secondary slotted disk (8) madial wall; Described wedge pawl pin axle (14) is provided with roller (13) on the axle head at the interior diapire place of secondary slotted disk (8), the outer of this roller (13) is tight against on the inner convex platform external cylindrical surface of secondary slotted disk (8), rotate around wedge pawl pin axle (14) under described roller (13) External Force Acting, this inner convex platform is positioned in the middle part of the diapire of secondary slotted disk (8), and the trapezoidal annular groove on inner convex platform and secondary slotted disk (8) madial wall has same axle center; Be fixed with torque spring (16) by spring pin (15) in the fluting of described voussoir (11), one end of this torque spring (16) is tight against on voussoir (11), and the other end of torque spring (16) is tight against in the deep-slotted chip breaker of connecting rod (12) waist; The predetermincd tension of described torque spring (16) and the bearing force of roller (13) are by the trapezoidal annular groove of the arc outer wedging of voussoir (11) on secondary slotted disk (8) madial wall.
2. bicycle use stepless change rear-guard axle according to claim 1, is characterized in that: described power intake (19) is positioned on one-level slotted disk (6), this one-level slotted disk (6) is provided with the input installation portion installed for power input; Described clutch end (20) is positioned on secondary stent (9), this secondary stent (9) is provided with the output installation portion installed for power output member.
3. bicycle use stepless change rear-guard axle according to claim 1, is characterized in that: the wedge claw assembly (10) in described wedge claw one-level speed-changing mechanism (C) is five groups with the wedge claw assembly (10) in wedge claw two stage speed change mechanism (D).
4. bicycle use stepless change rear-guard axle according to claim 1, it is characterized in that: the outer wall end of described speed governing ingress pipe (18) is fixed with a speed governing sheave (28), during use, this speed governing sheave (28) is connected with the swing handle in bicycle handle bar by the speed governing steel cable (27) of annular.
5. bicycle use stepless change rear-guard axle according to claim 1, is characterized in that: the ratio of number of teeth of described sun gear I (2101), planetary wheel I (2102), inner gear I (2103) is 4:1:6.
6. bicycle use stepless change rear-guard axle according to claim 1, is characterized in that: the ratio of number of teeth of described sun gear II (2201), planetary wheel II (2202), inner gear II (2203) is 8:7:22.
7. bicycle use stepless change rear-guard axle according to claim 1, is characterized in that: the ratio of number of teeth of described sun gear III (2301), planetary wheel III (2302), inner gear III (2303) is 5:2:9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520059613.2U CN204399435U (en) | 2015-01-28 | 2015-01-28 | Bicycle use stepless change rear-guard axle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520059613.2U CN204399435U (en) | 2015-01-28 | 2015-01-28 | Bicycle use stepless change rear-guard axle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204399435U true CN204399435U (en) | 2015-06-17 |
Family
ID=53423315
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520059613.2U Expired - Fee Related CN204399435U (en) | 2015-01-28 | 2015-01-28 | Bicycle use stepless change rear-guard axle |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN204399435U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104554609A (en) * | 2015-01-28 | 2015-04-29 | 孙晓雁 | Stepless variable speed rear drive shaft for bicycles |
-
2015
- 2015-01-28 CN CN201520059613.2U patent/CN204399435U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104554609A (en) * | 2015-01-28 | 2015-04-29 | 孙晓雁 | Stepless variable speed rear drive shaft for bicycles |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| KR200482156Y1 (en) | Planetary gear apparatus using two input characteristic and gear module thereof | |
| CN102762441B (en) | Electrically assisted bicycle | |
| US9079632B2 (en) | Gear and lever transmission system and method | |
| CN200997546Y (en) | Hub motor of double-speed electric automobile with positive and reversing rotation speed variation | |
| CA2677552C (en) | Continuously variable transmission | |
| US3429200A (en) | Automatic speed change transmission | |
| WO2018127737A1 (en) | Mechanism | |
| CN204399435U (en) | Bicycle use stepless change rear-guard axle | |
| US6447421B1 (en) | Device to provide continuously variable gearing | |
| US5590894A (en) | Bicycle drive device | |
| CN104554609A (en) | Stepless variable speed rear drive shaft for bicycles | |
| CN110657216B (en) | Mechanism for realizing cosine acceleration motion law and reverse solving method | |
| US9464696B2 (en) | Continuous variable transmission system and use thereof | |
| JPH09502242A (en) | Variable ratio power transmission device | |
| CN208587461U (en) | Gearbox and mobile platform | |
| WO2004040168A1 (en) | Stepless speed change apparatus | |
| JP2013108588A (en) | Continuously variable transmission | |
| CN105798900A (en) | Rope drive decoupling mechanism based on gear train and decoupling method thereof | |
| CN201672025U (en) | Mechanical stepless speed changer | |
| TWI434000B (en) | Connecting rod type stepless speed change device | |
| CN2823106Y (en) | Rolling type four gears stepless speed-changing bicycle | |
| CN101280838B (en) | Complete mechanical automatic stepless speed-changing device | |
| GB2421770A (en) | Stepless infinitely variable ratio gearbox | |
| CN104565250B (en) | Wedge claw stepless speed changing mechanism and transmission system | |
| EP2882981B1 (en) | A continuously variable gear ratio changing system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20150617 Termination date: 20170128 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |