CN102717705A - Mechanical intelligent adaptive double-gear automatic speed change hub with multiple cams - Google Patents
Mechanical intelligent adaptive double-gear automatic speed change hub with multiple cams Download PDFInfo
- Publication number
- CN102717705A CN102717705A CN2012102012663A CN201210201266A CN102717705A CN 102717705 A CN102717705 A CN 102717705A CN 2012102012663 A CN2012102012663 A CN 2012102012663A CN 201210201266 A CN201210201266 A CN 201210201266A CN 102717705 A CN102717705 A CN 102717705A
- Authority
- CN
- China
- Prior art keywords
- torus
- axial
- cam
- transmission shaft
- conical sleeve
- 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.)
- Granted
Links
Images
Landscapes
- Mechanical Operated Clutches (AREA)
- General Details Of Gearings (AREA)
Abstract
The invention discloses a mechanical intelligent adaptive double-gear automatic speed change hub with multiple cams The speed change hub comprises a power device, a box, a transmission shaft, wheels, a slow-gear transmission mechanism, a ring axial outer taper sleeve and a ring axial inner taper sleeve, wherein the ring axial outer taper sleeve is sleeved outside the transmission shaft and is in transmission via a spiral cam pair, and a slow-gear transmission structure with multiple end cams is employed for the slow-gear transmission mechanism. Since the mechanical intelligent adaptive double-gear automatic speed change hub with the multiple cams has all advantages of an existing adaptive automatic speed change mechanism and is provided with the slow-gear transmission structure with the multiple end cams, sensitivity in a gear-shifting process can be guaranteed, gear-shifting jerking and jamming feelings are eliminated, driving comfort is improved, energy is further saved, energy consumption is further lowered, and dynamic property, economical efficiency, driving safety and comfort of a vehicle are greatly improved.
Description
Technical field
The present invention relates to a kind of Vehicular hub, particularly a kind of mechanical intelligence self adaptation cam automatic gear shift hub more than two grades.
Background technology
In the prior art, automobile, motor bike, Electrical Bicycle all are through governor handle or acceleration pedal direct control throttle gate or current control speed basically, or adopt manual mechanical automatic transmission mode to realize speed change.The operation of navigating mate is depended in the operation of handle or acceleration pedal fully, usually can cause operation and garage's situation not to match, and the stall phenomenon appears in causes motor or driving engine fluctuation of service.
Self-propelled vehicle by rider under the situation of not knowing resistance to motion; The transmission system that only rule of thumb controls; Have following problem unavoidably: 1. when startup, upward slope and heavy load, because resistance to motion increases, force motor or engine speed to descend and work in the low efficiency district.2. owing to do not have mechanical transmission adjustment moment of torsion and speed, can only promote the use of, can not satisfy under mountain area, hills and the heavy load conditions and use, dwindle range of use at region of no relief; 3. drive wheel place installing space is little, has installed to be difficult to hold automatic transmission with hydraulic torque converter and other up-to-date technology behind driving engine or the motor again; 4. do not possess adaptive function, can not detect, revise and get rid of the operation mistake of chaufeur automatically; 5. change when unexpected in the speed of a motor vehicle, must cause motor or engine power and resistance to motion to be difficult to coupling.6. continuing, distance is short, hill climbing ability is poor, and applicable area is little.
In order to overcome the above problems; The application contriver has invented a series of cam self-adapting automatic gear shifting device; Utilize the resistance to motion power cam, reach self shifter and, have effect preferably according to the purpose of resistance to motion Adaptive matching speed of a motor vehicle output torque; Though aforesaid cam self-adapting automatic gear shifting device has above-mentioned advantage; Stability and high efficiency improve a lot than prior art; But the part component structural is comparatively complicated, and the change-speed box volume is bigger, simultaneously; Owing to adopted a plurality of cams (same circumference) structure, stability is still not ideal enough; And, influence the smoothness of self shifter process through having bite in the cam clutch process; Though on service life, increase,, still have room for improvement service life according to structural analysis than prior art.
Therefore; Need a kind of above-mentioned cam self-adapting automatic gear shifting device to be improved, not only can self adaptation do not cut off under the situation of propulsive effort and carry out shift speed change automatically, solve the little problem that can not satisfy road usage under the complex conditions of moment of torsion-rotation speed change with the change in resistance of going; Stationarity is good; Further increase work efficiency, have better energy conservation and consumption reduction effects, and reduce volume; Simultaneously, the smooth and easy no bite of shift process is quick on the draw, and practices thrift drive energy, cuts down the consumption of energy, and further improves service life, is applicable to that power actuated vehicle uses.
Summary of the invention
In view of this; The purpose of this invention is to provide a kind of mechanical intelligence self adaptation cam automatic gear shift hub more than two grades, not only can self adaptation do not cut off under the situation of propulsive effort and carry out shift speed change automatically, solve the little problem that can not satisfy road usage under the complex conditions of moment of torsion-rotation speed change with the change in resistance of going; Stationarity is good; Further increase work efficiency, have better energy conservation and consumption reduction effects, and reduce volume; Simultaneously, the smooth and easy no bite of shift process is quick on the draw, and practices thrift drive energy, cuts down the consumption of energy, and further improves service life, is applicable to that power actuated vehicle uses.
Mechanical intelligence self adaptation of the present invention cam automatic gear shift hub more than two grades; Comprise engine installation, casing, transmission shaft and wheel; Said transmission shaft is arranged in the casing and its normal-running fit; Transmission shaft outputs power and cooperates with the wheel transmission, also comprises keeping off transmission device slowly and being arranged on the mechanical intelligence adaptive rate assembly on the transmission shaft;
Mechanical intelligence adaptive rate assembly comprises the axial external conical sleeve of torus, the axial inner conical drogue of torus and speed change elastic element;
The axial inner conical drogue of said torus cooperates in the circumferencial direction transmission with the rotational power output block of engine installation; The axial inner conical drogue of torus is provided with axial inner conical surface and is coated at the axial external conical sleeve of torus, and the axial external conical sleeve of torus is provided with the axial male cone (strobilus masculinus) that matches with the axial inner conical surface of the axial inner conical drogue of torus; The axial external conical sleeve of said torus is coated at transmission shaft and cooperates through the auxiliary driving of main gear cam with it;
The speed change elastic element applies the predetermincd tension of the inner conical surface applying transmission that makes its male cone (strobilus masculinus) and the axial inner conical drogue of torus to the axial external conical sleeve of torus; During said transmission shaft takeoff output, main gear cam pair applies and the opposite axial component of speed change elastic element predetermincd tension the axial external conical sleeve of torus;
The said transmission device that keeps off slowly comprises the intermediate reduction gear transmission device that has overriding clutch, and the axial inner conical drogue of torus cooperates with the power intake transmission of intermediate reduction gear transmission device; Normal-running fit is coated at transmission shaft and is provided with an intermediate cam cover at least, and said intermediate cam is overlapped axial two ends and is respectively equipped with corresponding secondary with the axial external conical sleeve of torus and the intermediate reduction gear transmission device cooperates and will keep off power slowly is passed to the axial external conical sleeve of torus by the clutch end of intermediate reduction gear transmission device through cam-engaged.
Further, the axial inner conical surface of the axial inner conical drogue of torus or be provided with oilway with the axial male cone (strobilus masculinus) of the axial external conical sleeve of torus, this oilway is provided with the port that communicates with cabinets cavity;
Further; The axial male cone (strobilus masculinus) of the axial external conical sleeve of said torus is provided with oilway, and said oilway is left-handed and right hand helix shape interleaved discs and is around in axial male cone (strobilus masculinus) and its port and is coiled in axial male cone (strobilus masculinus) two ends with right hand helix and forms naturally by oilway is left-handed;
Further; The inner ring normal-running fit of overriding clutch is coated at transmission shaft; The intermediate reduction gear transmission device also comprises the train of reduction gears that is used for power is passed to by the axial inner conical drogue of torus overriding clutch; The inner ring of said overriding clutch surmounts between the takeoff output hand of rotation of transmission shaft and outer ring; The axial inner conical drogue of said torus cooperates with the outer ring transmission of overriding clutch through train of reduction gears, will keep off power slowly through the intermediate cam cover between the axial external conical sleeve of the inner ring of said overriding clutch and torus and be passed to the axial external conical sleeve of torus by the inner ring of overriding clutch; The cam-engaged pair at intermediate cam cover two ends is the edge type strainer Meshing Pair, and the shape line lift angle of its edge type strainer all varies in size smaller or equal to the shape line lift angle of 45 ° and intermediate cam cover two ends edge type strainer;
Further, said overriding clutch is the spring-piece type overriding clutch, comprises roller and retainer, is formed for the engaging groove that meshes or separate with roller between the outer ring of overriding clutch and the inner ring; Said retainer comprises supporting blade, pillar stiffener and reed; Said pillar stiffener is corresponding one by one with roller; Said supporting blade is arranged at pillar stiffener and between supporting blade and pillar stiffener outside face, forms slot in the circumferencial direction heavy keying fit; Said reed is provided with the fitting portion that embeds slot, and reed extends slot and along the engagement direction of engaging groove roller applied predetermincd tension, and said slot is provided with reed owing to roller applied the distortion allowance of elastic deformation that predetermincd tension produces;
Further, said fitting portion is provided with pressure-bearing portion, and said supporting blade is provided with pressure-bearing portion applied and makes fitting portion embed the pressure of slot and limit fitting portion from pressing portion that slot is deviate from;
Further, said pressure-bearing portion is formed in one in fitting portion and outward extending elastic piece structure, and pressure-bearing portion forms the pressure-bearing section to the bending of pressing portion, and pressing portion forms superimposed in pressure-bearing section outside face and pressing section that the pressure-bearing section is exerted pressure to the bending of pressure-bearing portion;
Further; Said train of reduction gears comprises keeps off tween drive shaft slowly, is arranged at keep off slowly that tween drive shaft cooperates with its transmission first keep off gear and second slowly and keep off gear slowly; The axial inner conical drogue of said torus keeps off meshed transmission gear slowly through keeping off driving gear and first slowly, and second keeps off the outer ring engaged transmission of gear and overriding clutch slowly;
Further; Said speed change elastic element is the speed change butterfly spring that is coated at transmission shaft; Said speed change butterfly spring and overriding clutch are respectively in the axial both sides of the axial external conical sleeve of torus; Speed change butterfly spring withstands axial external conical sleeve one axial end portion of torus through speed change axle sleeve and the speed change surface bearing that bearing fit is coated at transmission shaft successively, and another axial end portion of the axial external conical sleeve of torus cooperates through cooresponding edge type strainer auxiliary driving with the intermediate cam cover; Circle is provided with the inside spin cam in the axial external conical sleeve of torus, and transmission shaft is provided with the external spiral cam that matches with the inside spin cam and forms the spiral prominence wheel set jointly;
Further, said speed change butterfly spring is arranged on the right side of the axial external conical sleeve of torus, and overriding clutch is positioned at the axial external conical sleeve of torus left side; The expansion direction of the inside spin cam of the axial external conical sleeve of said torus and the external spiral cam of transmission shaft is identical with transmission shaft takeoff output hand of rotation from left to right; The inner ring of said intermediate cam cover two ends and overriding clutch and the axial external conical sleeve of torus are provided with edge type strainer respectively and through the edge type strainer formation edge type strainer Meshing Pair of intermeshing; The inner ring of intermediate cam cover two ends and overriding clutch is opposite with transmission shaft takeoff output hand of rotation from left to right with the edge type strainer pressure line expansion direction of the axial external conical sleeve of torus; Said engine installation is a motor, and the rotor of motor cooperates with the axial inner conical drogue transmission of torus through gear frame, and said gear frame is supported in transmission shaft through an annular bearing with rolling contact, in the cavity of said speed change butterfly spring between gear frame and transmission shaft cylindrical.
The invention has the beneficial effects as follows: mechanical intelligence self adaptation of the present invention cam automatic gear shift hub more than two grades; Whole advantages with existing cam self-adapting automatic gear shifting device; If can detect driving torque-rotating speed and resistance to motion-GES according to resistance to motion; Make motor or engine output and traveling state of vehicle be in the optimum matching state all the time; Realize the balance control of vehicular drive moment and comprehensive resistance to motion, self adaptation is carried out shift speed change automatically with the change in resistance of going under the situation of not cutting off propulsive effort; Can satisfy under mountain area, hills and the heavy load conditions and use, it is mild that motor or engine load are changed, and power actuated vehicle operates steadily, and improves safety;
Simultaneously, the present invention adopts the drive mechanism of retaining slowly of multiterminal face cam, can guarantee the sensitieness in shift process; Eliminate gearshift pause and transition in rhythm or melody sense and bite sense; Improve ride comfort, further save energy and reduce the cost, improve dynamic property, economy, drive safety and the traveling comfort of vehicle greatly.
Description of drawings
Below in conjunction with accompanying drawing and embodiment the present invention is further described.
Fig. 1 is an axial section structural representation of the present invention;
Fig. 2 is the axial external conical sleeve structure scheme drawing of torus;
Fig. 3 is the inner ring structural representation of overriding clutch;
Oil duct structural representation on the axial external conical sleeve conical surface of Fig. 4 torus;
Fig. 5 is an intermediate cam nested structure scheme drawing;
Fig. 6 launches scheme drawing for the cam at intermediate cam cover two ends;
Fig. 7 is the overriding clutch structural representation;
Fig. 8 is that pillar stiffener, supporting blade and reed cooperate scheme drawing;
Fig. 9 is the reed structure scheme drawing;
Figure 10 is the axial semi-sictional view structural representation of overriding clutch.
The specific embodiment
Fig. 1 is an axial section structural representation of the present invention, and Fig. 2 is the axial external conical sleeve structure scheme drawing of torus, and Fig. 3 is the inner ring structural representation of overriding clutch, oil duct structural representation on the axial external conical sleeve conical surface of Fig. 4 torus; Fig. 5 is an intermediate cam nested structure scheme drawing; Fig. 6 launches scheme drawing for the cam at intermediate cam cover two ends; Fig. 7 is the overriding clutch structural representation; Fig. 8 is that pillar stiffener, supporting blade and reed cooperate scheme drawing, and Fig. 9 is the reed structure scheme drawing, and Figure 10 is the axial semi-sictional view structural representation of overriding clutch; As shown in the figure: the engine installation of present embodiment is a motor; See left-hand revolution during work from left to right, motor is inner rotor motor, and is as shown in the figure; Stator 26 is fixed in casing, and rotor 27 outputs power;
Mechanical intelligence self adaptation of the present invention cam automatic gear shift hub more than two grades; Comprise engine installation, casing 3, transmission shaft 1 and wheel 5; Said transmission shaft 1 is arranged in the casing 3 and its normal-running fit; As shown in the figure, the transmission shaft two ends are supported in casing through annular bearing with rolling contact 30 and annular bearing with rolling contact 13 normal-running fiies respectively; Transmission shaft 1 outputs power and cooperates with wheel 5 transmissions; Transmission shaft 1 outputs power and cooperates with wheel 5 transmissions, and is as shown in the figure, and the drive mechanism that transmission shaft 1 extends casing and wheel 5 can adopt any transmission fit system of prior art; Can be directly at circumferencial direction captive joint or the like; As shown in the figure, wheel 5 is in transmission connection in transmission shaft 1 through middleware 38, and middleware 38 passes through spline fitted with transmission shaft 1; Transmission shaft 1 extends the end of casing 3 through the support normal-running fit of annular bearing with rolling contact 2 with braking mechanism; Also be provided with chain stay 4; The left leg pipe and the right leg pipe of chain stay 4 divide Train Wheel 5 left and right sides; The support of braking mechanism is connected with the left leg pipe of chain stay 4, all adopts the connection structure of prior art, repeats no more at this; Also comprise and keep off transmission device slowly and be arranged on the mechanical intelligence adaptive rate assembly on the transmission shaft;
Mechanical intelligence adaptive rate assembly comprises the axial external conical sleeve of torus 14, the axial inner conical drogue 17 of torus and speed change elastic element 28;
The axial inner conical drogue 17 of said torus cooperates in the circumferencial direction transmission with the rotational power output block of engine installation; The axial inner conical drogue 17 of torus is provided with axial inner conical surface and is coated at the axial external conical sleeve 14 of torus; The axial external conical sleeve 14 of torus is provided with the axial male cone (strobilus masculinus) that matches with the axial inner conical surface of the axial inner conical drogue of torus; Cooperate transmission through the tapered sleeve structure; Inner conical surface and male cone (strobilus masculinus) one of at least need have certain roughness, belongs to those skilled in the art and can know according to this record, repeats no more at this; The axial external conical sleeve 14 of said torus is coated at transmission shaft 1 and interior circle is provided with inside spin cam 14a, and transmission shaft 1 is provided with the external spiral cam 1a that matches with the inside spin cam and forms the spiral prominence wheel set jointly; The spiral prominence wheel set is the helicitic texture that cooperatively interacts; When the axial external conical sleeve 14 of torus rotates; Through the spiral prominence wheel set transmission shaft 1 is produced axially and two component of circumferencial direction; Wherein circumferencial direction component drives transmission shaft 1 and rotates also outputting power, and axial component is offset by the mounting structure of transmission shaft 1, and its reaction force acts is in the axial external conical sleeve 14 of torus and put on speed change elastic element 28; Certainly, the spiral prominence wheel set is the preferred structure of present embodiment, also can adopt the secondary driving of existing other cam, such as edge type strainer or the like; But the spiral prominence wheel set can make this structure more compact, make, install and keep in repair more convenient, and helical structure stable drive; Stressed evenly have unrivaled stability and smoothness, further increases work efficiency; Have better energy conservation and consumption reduction effects, bigger control vehicle discharging is applicable to that lighter roadsters such as two-wheel car use;
The axial external conical sleeve 14 of 28 pairs of torus of speed change elastic element applies the predetermincd tension of the inner conical surface applying transmission that makes its male cone (strobilus masculinus) and the axial inner conical drogue 17 of torus; During said transmission shaft 1 takeoff output, the spiral prominence wheel set applies and the opposite axial component of speed change elastic element 28 predetermincd tensions the axial external conical sleeve 14 of torus; That is to say; The rotation direction of the spiral cam of spiral prominence wheel set is relevant with the takeoff output rotation direction of transmission shaft; Those skilled in the art are according to above-mentioned record; Under the prerequisite of learning transmission shaft takeoff output direction, can learn that which kind of rotation direction of spiral cam can apply the axial component of which kind of direction, repeats no more at this;
The said transmission device that keeps off slowly comprises the intermediate reduction gear transmission device that has overriding clutch, and the axial inner conical drogue 17 of torus cooperates with the power intake transmission of intermediate reduction gear transmission device; Normal-running fit is coated at transmission shaft and is provided with intermediate cam cover 6 at least, and said intermediate cam cover 6 axial two ends are respectively equipped with corresponding through cam-engaged pair and the axial external conical sleeve 14 of torus and the intermediate reduction gear transmission device cooperates and will keep off power slowly is passed to the axial external conical sleeve 14 of torus by the clutch end of intermediate reduction gear transmission device; The cam-engaged pair can be that the edge type strainer Meshing Pair also can be the spiral cam Meshing Pair, all can realize goal of the invention; The overriding clutch of intermediate reduction gear transmission device can be arranged at any position of the messenger chain of this mechanism; All can realize purpose; The intermediate reduction gear transmission device can be primary gear speed reducing transmission or other reducing transmission structures, and this intermediate reduction gear transmission device can guarantee that rotating speed that the axial inner conical drogue 17 of torus is passed to the outer ring 15 of overriding clutch is lower than the rotating speed of the axial inner conical drogue 17 of torus; Simultaneously; Intermediate cam cover 6 also applies axial force to the axial external conical sleeve 14 of torus and makes 28 compressions of speed change elastic element when keeping off transmission slowly; Keep separating of axial external conical sleeve 14 of torus and the axial inner conical drogue 17 of torus, guarantee that keeping off transmission is not slowly interfered.
In the present embodiment, the axial inner conical surface of the axial inner conical drogue 17 of torus or be provided with oilway with the axial male cone (strobilus masculinus) of the axial external conical sleeve 14 of torus, this oilway is provided with the port that communicates with cabinets cavity; This oilway does not need other fuel feeding, directly utilizes the lubricating oil in the casing can realize lubricating; Port be generally positioned at the axial inner conical drogue of torus axial inner conical surface or with the axial end portion of the axial male cone (strobilus masculinus) of the axial external conical sleeve of torus, be beneficial to the formation circulatory lubrication.
In the present embodiment; The axial male cone (strobilus masculinus) of the axial external conical sleeve 14 of said torus is provided with oilway 9, and said oilway 9 is left-handed and right hand helix shape interleaved discs and is around in axial male cone (strobilus masculinus) and its port and is coiled in axial male cone (strobilus masculinus) two ends with right hand helix and forms naturally by oilway 9 is left-handed; As shown in Figure 4, oilway 9 be left-handed and right hand helix shape interleaved discs around, be circuitous coiled state; And the port of oilway 9 blocks formation naturally at the two ends of axial male cone (strobilus masculinus), owing to form the coiled coil structure, and port is positioned at axial two ends; When axial external conical sleeve 14 high speed rotating of torus; One port utilizes centnifugal force in oilway 9, to produce vacuum, and the another port then utilizes rotation to meet to lubricating oil and through vacuum lubricating oil is introduced oilway 9 from the port outflow, forms the circulation of lubricating oil; Thereby form the flushing effect, be beneficial to and take away impurity and heat; This circulation just not only makes and keeps clean between axial inner conical drogue 17 of torus and the axial external conical sleeve 14 of torus; Also be beneficial to and throw off and keep good relative motion when the two separates rapidly when keeping off transmission slowly; The generation of the heat of reducing friction is beneficial to the good running state that keeps entire mechanism.
In the present embodiment, inner ring 31 normal-running fiies of overriding clutch are coated at transmission shaft 1, and are as shown in the figure, and the surface that transmission shaft 1 cooperates with inner ring 31 is provided with oilway 7, guarantee the alerting ability that rotates; The intermediate reduction gear transmission device also comprises the train of reduction gears that is used for power is passed to by the axial inner conical drogue 17 of torus overriding clutch; The inner ring 31 of said overriding clutch surmounts between the takeoff output hand of rotation of transmission shaft 1 and outer ring 15; During with assurance height gear, keep off transmission device slowly and surmounted; The axial inner conical drogue of said torus 17 cooperates with outer ring 15 transmissions of overriding clutch through train of reduction gears, overlaps 6 through intermediate cam between the axial external conical sleeve 14 of the inner ring 31 of said overriding clutch and torus and will keep off power slowly and be passed to the axial external conical sleeve 14 of torus by the inner ring 31 of overriding clutch; The cam-engaged pair that intermediate cam is overlapped 6 two ends is the edge type strainer Meshing Pair; And the shape line lift angle that intermediate cam is overlapped the secondary edge type strainer of the cam-engaged at 6 two ends all varies in size smaller or equal to the shape line lift angle that 45 ° and intermediate cam are overlapped 6 two ends edge type strainers; As shown in the figure; The edge type strainer that intermediate cam is overlapped 6 two ends is respectively edge type strainer 6a and edge type strainer 6b, forms the edge type strainer Meshing Pair with the edge type strainer 31a of the inner ring 31 of overriding clutch and the edge type strainer 14b engagement of the axial external conical sleeve 14 of torus respectively; Edge type strainer is beneficial to and reduces radial dimension, is applicable to that dilly uses; Edge type strainer shape line lift angle is beneficial to less than 45 ° and forms enough big axial component and circumferential propulsive effort, and can avoid bite; The shape line lift angle that intermediate cam is overlapped 6 two ends edge type strainers varies in size; That is to say; Big another lift angle of lift angle is little, as shown in the figure, with the lift angle α of the edge type strainer ingear edge type strainer 6a of the inner ring 31 of overriding clutch less than with the lift angle β of the edge type strainer ingear edge type strainer 6a of the axial external conical sleeve 14 of torus; The circumferential propulsive effort of the assurance of lift angle β, and the assurance circumferential misalignment of lift angle α and realize that sensitive axis to the axial external conical sleeve 14 of torus is to driving.
In the present embodiment, said overriding clutch is the spring-piece type overriding clutch, comprises roller 33 and retainer, is formed for the engaging groove that meshes or separate with roller between the outer ring 15 of overriding clutch and the inner ring 31; Said retainer comprises supporting blade 36, pillar stiffener 35 and reed 34; Said pillar stiffener 35 is corresponding one by one with roller 33; Said supporting blade 36 is arranged at pillar stiffener 35 and between supporting blade 36 and pillar stiffener 35 outside faces, forms slot 37 in the circumferencial direction heavy keying fit; Said reed 34 is provided with the fitting portion 34a that embeds slot 37; Reed 34 extends slot 37 and along the engagement direction of engaging groove roller 33 is applied predetermincd tension, and said slot 37 is provided with reed 34 owing to roller 33 applied the distortion allowance of elastic deformation that predetermincd tension produces; The overriding clutch of this structure is avoided on outer ring 15, directly processing limit base, simplifies the course of processing, increases work efficiency; Cut down finished cost, guarantee processing and assembly precision, and be different from the structure of concentrating attachment point in the prior art; Do not adopt spot welded fixed sturcture, the consequence that metallographic structure changes can not take place, eliminated since the engagement of overriding clutch with separates elasticity of spring leaf and is out of shape the stress concentration that causes; And make reed 34 have freedom of movement preferably; Thereby can improve the consequently operation life of whole overriding clutch of reed 34, reed can reach the elastic deformation that has predetermincd tension more than 5,000,000 times, reduces greatly and uses and maintenance cost; Associated components of the present invention damages the back and changes easily, and outer ring 15 does not need integral body to scrap, and reduces maintenance and use cost; Owing to adopt the retainer structure beyond the outer ring 15; The axial length that can theory unlimited prolongs overriding clutch and roller 33, the increase length of action that is to say; Can increase the axial length of overriding clutch according to the load-bearing needs; Thereby increase the load-carrying capacity of overriding clutch, and reduce to prolong the service life of overriding clutch than the overriding clutch radial dimension under the high bearing capacity; Simultaneously; Because reed is for distribute vertically; Thereby can carry out multiple spot to roller as required and apply predetermincd tension, guarantee than major axis spacing balance to roller under the prerequisite of size, make it not depart from parallel with inner ring axis; Thereby guarantee the smooth operation of overriding clutch, avoid mechanical breakdown;
As shown in the figure; Said supporting blade 36 is along circumferentially being wrapped in pillar stiffener 35 and setting and hold predetermincd tension tightly; The cross-sectional plane of said pillar stiffener 35 is circumferentially non-circular in relative rotation for limiting supporting blade 36, forms slot 37 between a side of supporting blade 36 and pillar stiffener 35 1 side surfaces; The cross-sectional plane of pillar stiffener 35 adopts polymorphic structure, and supporting blade 36 can limit it along circumferentially rotating after being wrapped in pillar stiffener 35, and is simple in structure; Enforcement, easy accessibility utilize non-circular structure to limit the circumferential movement of supporting blade 36, form comparatively stable slot 37 structures; For the installation of reed 34 provides condition; Do not need other mechanical fixed structure, avoid guaranteeing its service life because structures such as spot welding form the mechanical force to reed; As shown in the figure, the polymorphic structure of pillar stiffener 35 cross-sectional planes for constituting by circular arc and straight line, and supporting blade 36 is wrapped in the polymorphic structure periphery, makes it not have condition in relative rotation.
In the present embodiment, said fitting portion 34a is provided with the 34b of pressure-bearing portion, and said supporting blade 36 is provided with the 34a of pressure-bearing portion applied and makes fitting portion 34a embed the pressure of slot 37 and limit fitting portion 34a from the 36a of pressing portion that slot is deviate from; Guarantee when avoiding fitting portion 34a to deviate from that reed 34 has degree of freedom swing preferably, prolongs its service life.
In the present embodiment; The said pressure-bearing 34b of portion is formed in one in fitting portion 34a and outward extending elastic piece structure; The 34b of pressure-bearing portion forms pressure-bearing section 34c to the 36a of pressing portion bending, and the 36a of pressing portion forms superimposed in pressure-bearing section 34c outside face and pressing section 36b that pressure-bearing section 34c is exerted pressure to the 34b of pressure-bearing portion bending; This pressure makes fitting portion be embedded in slot 37, forms to stablize embedded structure; As shown in the figure, the rounding off structure is adopted in bending, avoids stress concentration; Directly slip into through external force during installation and the pressure-bearing section is superimposed in the pressing section, utilize pressure-bearing section self elasticity to form insertion force, simple in structure; Easy for installation, can't produce bigger distortion and stress concentration.
As shown in the figure; Said retainer also comprises pushing out ring I 32 and pushing out ring II 24; Said pushing out ring I 32 and pushing out ring II 15 axial two ends, 24 apportion outer rings and with outer ring 15 in the circumferencial direction heavy keying fit; Said pillar stiffener 4 two ends correspondence respectively are supported in pushing out ring I 32 and pushing out ring II 24, pillar stiffener 35 in self circumferencial direction and pushing out ring I 32 or/and pushing out ring II 24 heavy keying fit; After the assembling, pushing out ring I 32 and pushing out ring II 24 can be passed through screw, riveted and fixed in the outer ring 15, also can be fixed in outer ring 15 to its axial limiting through other parts; As shown in the figure, pillar stiffener 35 is parallel to roller 33; Engaging groove engagement direction is the direction that engaging groove shoals gradually, the direction that the engagement space of engaging groove and inner ring 31 cylindricals formation just narrows down gradually; The elasticity of reed 34 enough avoids roller oppositely to mesh when overriding clutch surmounts; As shown in the figure; Said pillar stiffener 35 axial ends form flat axle and penetrate the structure of the flat hole of pushing out ring I 32 with formation circumferencial direction heavy keying fit through flat axle correspondence; Simple in structure, realize easily, and owing to form the shaft shoulder between flat axle and pillar stiffener 35 bodies; Thereby better positioning effect is arranged, be beneficial to assembling and keep running state preferably; The pillar stiffener 35 axial other ends pass the circular hole on the pushing out ring II 24, and the end that pillar stiffener passes the circular hole on the pushing out ring II forms conical head, and the conehead structure has comformability preferably, is beneficial to penetrate assembling, increases work efficiency.
Said pushing out ring I 32 is all processed sliding bearing structure with pushing out ring II 24; As shown in the figure; 15 axial two ends, said outer ring form deep gouge (deep gouge 15a as shown in the figure and deep gouge 15b) respectively; The radial groove (radial groove 15a and radial groove 15b) at 15 axial two ends, said outer ring is arranged at circle in the cooresponding deep gouge cell wall respectively; Said pushing out ring I 32 and the corresponding respectively deep gouge that embeds of pushing out ring II 24; Pushing out ring I 32 is respectively equipped with pushing out ring II 24 and is used for the corresponding radial protrusion (radial protrusion 32a and radial protrusion 24a) that embeds radial groove (radial groove 15a and radial groove 15b); The radial protrusion (radial protrusion 32a and radial protrusion 24a) of pushing out ring I 32 and pushing out ring II 24 and corresponding radial groove (radial groove 15a and radial groove 15b) over against, push vertically and get final product; It is stable with assembling between outer ring 15 and inner ring 31, to form the compact conformation that supports and be beneficial to the maintenance retainer, can not disturb because of external force to come off; Simultaneously, be beneficial to smooth operation between outer ring and the inner ring.
In the present embodiment; Said intermediate reduction gear transmission device comprises and keeps off tween drive shaft 18 slowly, is arranged at keep off slowly that tween drive shaft 18 cooperates with its transmission first keep off gear 20 and second slowly and keep off gear 19 slowly; As shown in the figure, keep off slowly tween drive shaft 18 through annular bearing with rolling contact 22 and annular bearing with rolling contact 16 normal-running fiies in casing 3; The axial inner conical drogue 17 of said torus keeps off gear 20 engaged transmission slowly through keeping off driving gear 10 and first slowly; As shown in the figure; The axial inner conical drogue 17 of torus is in transmission connection in keeping off outer ring 15 engaged transmission that driving gear 10, the second keeps off gear 19 and overriding clutch slowly slowly through other type of drive of end face spline or prior art; Simple and compact for structure, realize the transmission of power of retaining slowly.
In the present embodiment; Said speed change elastic element 28 is for being coated at the speed change butterfly spring of transmission shaft 1; The inner ring 31 of said speed change butterfly spring and overriding clutch is respectively in the axial both sides of the axial external conical sleeve 14 of torus; Speed change butterfly spring withstands axial external conical sleeve 14 1 axial end portions of torus through the speed change axle sleeve 21 that bearing fit is coated at transmission shaft 1, and axial external conical sleeve 14 another axial end portions of torus and intermediate cam cover 6 cooperates through cooresponding edge type strainer auxiliary driving; Simple in structure, arrangement space is little, utilizes the transfer route reasonable Arrangement parts of power, makes the present invention more be applicable to the use of less space.
In the present embodiment, said speed change butterfly spring is arranged on the right side of the axial external conical sleeve 14 of torus, and overriding clutch is positioned at the axial external conical sleeve of torus 14 left sides; The expansion direction of the inside spin cam of the axial external conical sleeve 14 of said torus and the external spiral cam of transmission shaft 1 is identical with transmission shaft takeoff output hand of rotation from left to right; The inner ring 31 that said intermediate cam is overlapped 6 two ends and overriding clutch is provided with edge type strainer respectively with the axial external conical sleeve 14 of torus and intermeshes through edge type strainer and forms the edge type strainer Meshing Pair; As shown in the figure; Slowly keep off driving gear 10 normal-running fiies and be coated at intermediate cam cover 6, axial inner conical drogue 17 cylindricals of torus pass through annular bearing with rolling contact 23 in casing 3; The edge type strainer 31a of the inner ring 31 of overriding clutch, the edge type strainer 14b of the axial external conical sleeve 14 of torus cooperates between edge type strainer 14b and edge type strainer 31a and the intermediate cam cover 6 to form the edge type strainer pair, is used for transmission; As shown in the figure; Inner ring 31 cylindricals of overriding clutch are positioned at the overriding clutch right side and are provided with annular boss; This annular boss is provided with surface bearing 8 and spacing ring 11 successively with keeping off driving gear 10 slowly, and it is carried out axial limiting, and inner ring 31 left ends of overriding clutch are provided with surface bearing 11; And through machinery realization is installed and locatees, reach its more stable axial limiting; The edge type strainer pressure line expansion direction of inner ring 31 and the axial external conical sleeve 14 of torus that intermediate cam is overlapped 6 two ends and overriding clutch is opposite with transmission shaft takeoff output hand of rotation from left to right; Said engine installation is a motor, and the rotor 27 of motor cooperates with axial inner conical drogue 17 transmissions of torus through gear frame 25, generally adopts the mode of captive joint; Said gear frame 25 is supported in transmission shaft 1 through an annular bearing with rolling contact 29, in the cavity of said speed change butterfly spring between gear frame 25 and transmission shaft 1 cylindrical.
Above embodiment is an optimum structure of the present invention, is not the qualification to protection domain of the present invention; Such as, motor also is not limited to inner rotor motor, also can be external rotor electric machine, just adjustment to some extent on connection mode, or the like some technical characterictics all can make corresponding change, and do not influence the realization of this goal of the invention.
The fast retaining power transmission line of present embodiment:
The external spiral cam 1a → wheel 5 of the inside spin cam 14a → transmission shaft 1 of the axial external conical sleeve of the axial external conical sleeve 14 → torus of the axial inner conical drogue 17 → torus of rotor 27 → torus;
This moment, overriding clutch surmounted, and the resistance transfer route: the axial external conical sleeve 14 of inside spin cam 14a → torus of the axial external conical sleeve of external spiral cam 1a → torus of transmission shaft 1 → transmission shaft 1 → compression speed change butterfly spring; The external spiral cam 1a of transmission shaft through transmission shaft 1 applies axial force and compresses speed change butterfly spring the inside spin cam 14a and the axial external conical sleeve 14 of torus of the axial external conical sleeve of torus; When resistance to motion is increased to one regularly; This axial force speed change butterfly spring; The axial inner conical drogue 17 of torus is separated with the axial external conical sleeve 14 of torus, and power promptly keeps off power transmission line slowly through following route transmission:
The axial inner conical drogue 17 of rotor 27 → torus → keep off slowly driving gear 10 → the first keeps off the external spiral cam 1a → wheel 5 of inside spin cam 14a → transmission shaft 1 that gear 20 → keep off slowly tween drive shaft 18 → the second keeps off the axial external conical sleeve of outer ring 15 → overriding clutch inner ring, 31 → intermediate cam cover axial external conical sleeve 14 → torus of 6 → torus of gear 19 → overriding clutch slowly slowly.
Slowly keep off power transmission line and also pass through following route simultaneously: the axial external conical sleeve 14 of intermediate cam cover 6 → torus → compression speed change butterfly spring; Prevent to keep off slowly the past compound compression of appearance compression speed change butterfly spring in the transmission process, thereby prevent axial external conical sleeve 14 applyings of axial inner conical drogue 17 of torus and torus.
There is above-mentioned transfer route to find out; The present invention is when operation; The male cone (strobilus masculinus) of the inner conical surface of the axial inner conical drogue 17 of torus and the axial external conical sleeve 14 of torus fits tightly under the effect of speed change butterfly spring, forms an automatic transmission that keeps certain pressure, and can adjust the required pressure of clutches engaged through the axial width that increases speed change axle sleeve 21; Reach the transmission purpose; At this moment, rotor drives the axial external conical sleeve of the axial inner conical drogue of torus 17, torus 14, transmission shaft 1, makes wheel 5 left-hand revolutions; Slowly keeping off overriding clutch this moment is in and surmounts state.
Resistance is greater than propulsive effort during motor vehicle starting, and resistance forces transmission shaft 1 to clockwise rotate certain angle, under the effect of the external spiral cam 1a of transmission shaft 1, and the axial external conical sleeve 14 compression speed change butterfly springs of torus; The axial external conical sleeve 14 of torus separates with the axial inner conical drogue 17 of torus; Synchronously; Slowly keep off the overriding clutch engagement; The transmission rotor drives the axial inner conical drogue 17, first of torus and keeps off gear 20 slowly, keeps off the axial external conical sleeve of outer ring 15, inner ring 31, intermediate cam cover 6, torus that tween drive shaft 18, second keeps off gear 19, overriding clutch slowly 14, transmission shaft 1 slowly, and wheel 5 is rotated with retaining speed slowly; Therefore, realize the bottom gear starting automatically, shortened cranking time, reduced starting power.Meanwhile, speed change butterfly spring absorbs movement resistor moment energy, holds potential energy fully for recovering soon the gear transferring power.
After starting successfully; Resistance to motion reduces; When component is reduced to less than the pressure that speed change butterfly spring produced; Discharge rapidly and promote down because of passive movement resistance compression produces speed change butterfly spring pressure, accomplish the male cone (strobilus masculinus) of the axial external conical sleeve 14 of torus and the inner conical surface recovery of the axial inner conical drogue 17 of torus and fit tightly state, keep off overriding clutch slowly and be in and surmount state.
In the driving process,, under the situation that need not cut off propulsive effort, realize becoming retaining, make whole locomotive operation steady along with the variation self shifter principle of resistance of motion is the same, safe and low consumption, and also transfer route is oversimplified the raising driving efficiency.
Explanation is at last; Above embodiment is only unrestricted in order to technical scheme of the present invention to be described; Although with reference to preferred embodiment the present invention is specified, those of ordinary skill in the art should be appreciated that and can make amendment or be equal to replacement technical scheme of the present invention; And not breaking away from the spirit and the scope of technical scheme of the present invention, it all should be encompassed in the middle of the claim scope of the present invention.
Claims (10)
1. mechanical intelligence self adaptation cam automatic gear shift hub more than two grades; Comprise engine installation, casing, transmission shaft and wheel; Said transmission shaft is arranged in the casing and its normal-running fit; Transmission shaft outputs power and cooperates with the wheel transmission, it is characterized in that: also comprise and keep off transmission device slowly and be arranged on the mechanical intelligence adaptive rate assembly on the transmission shaft;
Mechanical intelligence adaptive rate assembly comprises the axial external conical sleeve of torus, the axial inner conical drogue of torus and speed change elastic element;
The axial inner conical drogue of said torus cooperates in the circumferencial direction transmission with the rotational power output block of engine installation; The axial inner conical drogue of torus is provided with axial inner conical surface and is coated at the axial external conical sleeve of torus, and the axial external conical sleeve of torus is provided with the axial male cone (strobilus masculinus) that matches with the axial inner conical surface of the axial inner conical drogue of torus; The axial external conical sleeve of said torus is coated at transmission shaft and cooperates through the auxiliary driving of main gear cam with it;
The speed change elastic element applies the predetermincd tension of the inner conical surface applying transmission that makes its male cone (strobilus masculinus) and the axial inner conical drogue of torus to the axial external conical sleeve of torus; During said transmission shaft takeoff output, main gear cam pair applies and the opposite axial component of speed change elastic element predetermincd tension the axial external conical sleeve of torus;
The said transmission device that keeps off slowly comprises the intermediate reduction gear transmission device that has overriding clutch, and the axial inner conical drogue of torus cooperates with the power intake transmission of intermediate reduction gear transmission device; Normal-running fit is coated at transmission shaft and is provided with an intermediate cam cover at least, and said intermediate cam is overlapped axial two ends and is respectively equipped with corresponding secondary with the axial external conical sleeve of torus and the intermediate reduction gear transmission device cooperates and will keep off power slowly is passed to the axial external conical sleeve of torus by the clutch end of intermediate reduction gear transmission device through cam-engaged.
2. mechanical intelligence self adaptation according to claim 1 cam automatic gear shift hub more than two grades; It is characterized in that: the axial inner conical surface of the axial inner conical drogue of torus or be provided with oilway with the axial male cone (strobilus masculinus) of the axial external conical sleeve of torus, this oilway is provided with the port that communicates with cabinets cavity.
3. mechanical intelligence self adaptation according to claim 2 cam automatic gear shift hub more than two grades; It is characterized in that: the axial male cone (strobilus masculinus) of the axial external conical sleeve of said torus is provided with oilway, and said oilway is left-handed and right hand helix shape interleaved discs and is around in axial male cone (strobilus masculinus) and its port and is coiled in axial male cone (strobilus masculinus) two ends with right hand helix and forms naturally by oilway is left-handed.
4. mechanical intelligence self adaptation according to claim 3 cam automatic gear shift hub more than two grades; It is characterized in that: the inner ring normal-running fit of overriding clutch is coated at transmission shaft; The intermediate reduction gear transmission device also comprises the train of reduction gears that is used for power is passed to by the axial inner conical drogue of torus overriding clutch; The inner ring of said overriding clutch surmounts between the takeoff output hand of rotation of transmission shaft and outer ring; The axial inner conical drogue of said torus cooperates with the outer ring transmission of overriding clutch through train of reduction gears, will keep off power slowly through the intermediate cam cover between the axial external conical sleeve of the inner ring of said overriding clutch and torus and be passed to the axial external conical sleeve of torus by the inner ring of overriding clutch; The cam-engaged pair at intermediate cam cover two ends is the edge type strainer Meshing Pair, and the shape line lift angle of its edge type strainer all varies in size smaller or equal to the shape line lift angle of 45 ° and intermediate cam cover two ends edge type strainer.
5. mechanical intelligence self adaptation according to claim 4 cam automatic gear shift hub more than two grades; It is characterized in that: said overriding clutch is the spring-piece type overriding clutch; Comprise roller and retainer, be formed for the engaging groove that meshes or separate with roller between the outer ring of overriding clutch and the inner ring; Said retainer comprises supporting blade, pillar stiffener and reed; Said pillar stiffener is corresponding one by one with roller; Said supporting blade is arranged at pillar stiffener and between supporting blade and pillar stiffener outside face, forms slot in the circumferencial direction heavy keying fit; Said reed is provided with the fitting portion that embeds slot, and reed extends slot and along the engagement direction of engaging groove roller applied predetermincd tension, and said slot is provided with reed owing to roller applied the distortion allowance of elastic deformation that predetermincd tension produces.
6. mechanical intelligence self adaptation according to claim 5 cam automatic gear shift hub more than two grades; It is characterized in that: said fitting portion is provided with pressure-bearing portion, and said supporting blade is provided with pressure-bearing portion applied and makes fitting portion embed the pressure of slot and limit fitting portion from pressing portion that slot is deviate from.
7. mechanical intelligence self adaptation according to claim 6 cam automatic gear shift hub more than two grades; It is characterized in that: said pressure-bearing portion is formed in one in fitting portion and outward extending elastic piece structure; Pressure-bearing portion forms the pressure-bearing section to pressing portion bending, and pressing portion forms superimposed in pressure-bearing section outside face and pressing section that the pressure-bearing section is exerted pressure to the bending of pressure-bearing portion.
8. mechanical intelligence self adaptation according to claim 7 cam automatic gear shift hub more than two grades; It is characterized in that: said train of reduction gears comprises keeps off tween drive shaft slowly, is arranged at keep off slowly that tween drive shaft cooperates with its transmission first keep off gear and second slowly and keep off gear slowly; The axial inner conical drogue of said torus keeps off meshed transmission gear slowly through keeping off driving gear and first slowly, and second keeps off the outer ring engaged transmission of gear and overriding clutch slowly.
9. mechanical intelligence self adaptation according to claim 8 cam automatic gear shift hub more than two grades; It is characterized in that: said speed change elastic element is the speed change butterfly spring that is coated at transmission shaft; Said speed change butterfly spring and overriding clutch are respectively in the axial both sides of the axial external conical sleeve of torus; Speed change butterfly spring withstands axial external conical sleeve one axial end portion of torus through speed change axle sleeve and the speed change surface bearing that bearing fit is coated at transmission shaft successively, and another axial end portion of the axial external conical sleeve of torus cooperates through cooresponding edge type strainer auxiliary driving with the intermediate cam cover; Circle is provided with the inside spin cam in the axial external conical sleeve of torus, and transmission shaft is provided with the external spiral cam that matches with the inside spin cam and forms the spiral prominence wheel set jointly.
10. mechanical intelligence self adaptation according to claim 9 cam automatic gear shift hub more than two grades is characterized in that: said speed change butterfly spring is arranged on the right side of the axial external conical sleeve of torus, and overriding clutch is positioned at the axial external conical sleeve of torus left side; The expansion direction of the inside spin cam of the axial external conical sleeve of said torus and the external spiral cam of transmission shaft is identical with transmission shaft takeoff output hand of rotation from left to right; The inner ring of said intermediate cam cover two ends and overriding clutch and the axial external conical sleeve of torus are provided with edge type strainer respectively and through the edge type strainer formation edge type strainer Meshing Pair of intermeshing; The inner ring of intermediate cam cover two ends and overriding clutch is opposite with transmission shaft takeoff output hand of rotation from left to right with the edge type strainer pressure line expansion direction of the axial external conical sleeve of torus; Said engine installation is a motor, and the rotor of motor cooperates with the axial inner conical drogue transmission of torus through gear frame, and said gear frame is supported in transmission shaft through an annular bearing with rolling contact, in the cavity of said speed change butterfly spring between gear frame and transmission shaft cylindrical.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210201266.3A CN102717705B (en) | 2012-06-18 | 2012-06-18 | Mechanical intelligent adaptive double-gear automatic speed change hub with multiple cams |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210201266.3A CN102717705B (en) | 2012-06-18 | 2012-06-18 | Mechanical intelligent adaptive double-gear automatic speed change hub with multiple cams |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102717705A true CN102717705A (en) | 2012-10-10 |
| CN102717705B CN102717705B (en) | 2015-07-22 |
Family
ID=46943632
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210201266.3A Active CN102717705B (en) | 2012-06-18 | 2012-06-18 | Mechanical intelligent adaptive double-gear automatic speed change hub with multiple cams |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102717705B (en) |
Cited By (29)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105090485A (en) * | 2015-09-08 | 2015-11-25 | 西南大学 | Lateral hanging spiral type taper sleeve transmission self-adaptation automatic speed changing drive assembly of electric motor car |
| CN105090487A (en) * | 2015-09-08 | 2015-11-25 | 梁稚子 | Internal rotor concave-convex friction driven adaptive automatic transmission driving assembly of electric motorcycle |
| CN105090484A (en) * | 2015-09-08 | 2015-11-25 | 西南大学 | Electric motorcycle inner rotor motor spiral taper sleeve driving self-adaption automatic transmission drive assembly |
| CN105090421A (en) * | 2015-09-08 | 2015-11-25 | 西南大学 | Bow cone type two-gear self-adaptation automatic variable speed driving assembly for external rotor motor of electric motorcycle |
| CN105090486A (en) * | 2015-09-08 | 2015-11-25 | 西南大学 | Outer rotor motor spiral type taper sleeve transmission self-adaptation automatic speed changing drive assembly of electric motor car |
| CN105114614A (en) * | 2015-09-21 | 2015-12-02 | 西南大学 | Spiral type triangular friction transmission self-adaptation automatic variable speed drive assembly of electric motorcycle |
| CN105114572A (en) * | 2015-09-08 | 2015-12-02 | 梁稚子 | Electric motorcycle external rotor motor biconical friction transmission self-adaptive automatic speed-changing drive assembly |
| CN105114615A (en) * | 2015-09-08 | 2015-12-02 | 梁稚子 | Electric motorcycle internal rotor motor biconical friction transmission self-adaptive automatic speed-changing drive assembly |
| CN105129016A (en) * | 2015-09-09 | 2015-12-09 | 西南大学 | Side-hung bow cone swing type self-adaption automatic variable-speed drive assembly for electric motorcycle |
| CN105156658A (en) * | 2015-09-09 | 2015-12-16 | 梁稚子 | Inner rotor motor swing type self-adaption automatic variable speed drive assembly of electric motor car |
| CN105156662A (en) * | 2015-09-08 | 2015-12-16 | 西南大学 | Waveform friction transmission self-adaption automatic speed change drive assembly of external rotor electric machine of electric motorcycle |
| CN105156617A (en) * | 2015-09-08 | 2015-12-16 | 梁稚子 | Concave-convex type friction drive side hanging type self-adaption automatic variable speed drive assembly of electric motor car |
| CN105156663A (en) * | 2015-09-08 | 2015-12-16 | 西南大学 | Inner rotor motor wave-shaped friction transmission self-adaption automatic variable speed drive assembly of electric motor car |
| CN105156618A (en) * | 2015-09-09 | 2015-12-16 | 西南大学 | External rotor motor cyrtoconic swing type self-adaption automatic variable speed drive assembly of electric motor car |
| CN105172991A (en) * | 2015-09-08 | 2015-12-23 | 梁稚子 | Bow disc type two-gear self-adaption automatic speed change drive assembly of inner rotor motor of electric motorcycle |
| CN105221734A (en) * | 2015-09-09 | 2016-01-06 | 梁稚子 | Battery-operated motor cycle external rotor electric machine pendulum-type self-adapting automatic gear shift drives assembly |
| CN105253245A (en) * | 2015-09-08 | 2016-01-20 | 梁稚子 | Electric motor car external rotor electric machine concave-convex friction drive self-adaption automatic transmission drive assembly |
| CN105270562A (en) * | 2015-09-09 | 2016-01-27 | 梁稚子 | Side-hanging pendulum type self-adaptive automatic transmission driving assembly for electric motorcycle |
| CN105299217A (en) * | 2015-09-09 | 2016-02-03 | 西南大学 | Pendulum type self-adaption automatic variable speed drive assembly of electric motorcycle inner rotor motor bow cone |
| CN105370835A (en) * | 2015-09-08 | 2016-03-02 | 梁稚子 | Bow cone type two-gear self-adaptation automatic speed changing drive assembly of inner rotor motor of electric motorcycle |
| CN105370875A (en) * | 2015-09-08 | 2016-03-02 | 梁稚子 | Bow disc type two-gear self-adaptation automatic speed changing drive assembly of outer rotor motor of electric motorcycle |
| CN105711409A (en) * | 2016-01-27 | 2016-06-29 | 柳超 | Three-gear speed change wheel based on cam gear shifting |
| CN110005801A (en) * | 2019-04-16 | 2019-07-12 | 西南大学 | Double mechanical shaft end output adaptive automatic transmission of overdrive clutch |
| CN110017370A (en) * | 2019-04-18 | 2019-07-16 | 西南大学 | The mechanical double overdrive clutch self-adapting automatic gear shift main shaft assembly of planetary system output |
| CN110014829A (en) * | 2019-04-16 | 2019-07-16 | 西南大学 | Double mechanical shaft end output adaptive fluid drive power drive systems of overdrive clutch |
| CN110017369A (en) * | 2019-04-17 | 2019-07-16 | 西南大学 | Double overdrive clutch axle sleeve output adaptive automatic transmission of planetary gear train input |
| CN110185790A (en) * | 2019-04-16 | 2019-08-30 | 西南大学 | Double mechanical axle sleeve output adaptive fluid drive power drive systems of overdrive clutch |
| CN110193572A (en) * | 2019-06-27 | 2019-09-03 | 马鞍山钢铁股份有限公司 | The manufacturing method of double S type web wheel press shaping die devices and double S type web wheels |
| WO2020211696A1 (en) * | 2019-04-16 | 2020-10-22 | 西南大学 | Dual-overrunning clutch shaft sleeve output adaptive automatic transmission main shaft assembly, gearbox, and drive system |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008044587A (en) * | 2006-08-18 | 2008-02-28 | Junichi Yoshimori | Overrunning clutch enabling hybrid function and generator and drive motor with built-in deceleration gear |
| CN101244752A (en) * | 2008-03-03 | 2008-08-20 | 西南大学 | Side-hanging taper disc type self-adaption two-gear automatic speed changing hub |
| CN101323252A (en) * | 2008-06-18 | 2008-12-17 | 西南大学 | Cone-disk clutch cam self-adapting automatic transmission hub |
| CN101526114A (en) * | 2009-03-31 | 2009-09-09 | 西南大学 | Double cam self-adapting automatic clutch |
| CN101525034A (en) * | 2009-03-31 | 2009-09-09 | 西南大学 | Double cam self-adapting automatic gear shifting hub |
| US20110015030A1 (en) * | 2007-08-31 | 2011-01-20 | Southwest University | cam self-adaptive automatic speed shift hub |
| CN102287459A (en) * | 2011-07-21 | 2011-12-21 | 西南大学 | Heavy-duty overrunning clutch |
-
2012
- 2012-06-18 CN CN201210201266.3A patent/CN102717705B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008044587A (en) * | 2006-08-18 | 2008-02-28 | Junichi Yoshimori | Overrunning clutch enabling hybrid function and generator and drive motor with built-in deceleration gear |
| US20110015030A1 (en) * | 2007-08-31 | 2011-01-20 | Southwest University | cam self-adaptive automatic speed shift hub |
| CN101244752A (en) * | 2008-03-03 | 2008-08-20 | 西南大学 | Side-hanging taper disc type self-adaption two-gear automatic speed changing hub |
| CN101323252A (en) * | 2008-06-18 | 2008-12-17 | 西南大学 | Cone-disk clutch cam self-adapting automatic transmission hub |
| CN101526114A (en) * | 2009-03-31 | 2009-09-09 | 西南大学 | Double cam self-adapting automatic clutch |
| CN101525034A (en) * | 2009-03-31 | 2009-09-09 | 西南大学 | Double cam self-adapting automatic gear shifting hub |
| CN102287459A (en) * | 2011-07-21 | 2011-12-21 | 西南大学 | Heavy-duty overrunning clutch |
Cited By (33)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105172991A (en) * | 2015-09-08 | 2015-12-23 | 梁稚子 | Bow disc type two-gear self-adaption automatic speed change drive assembly of inner rotor motor of electric motorcycle |
| CN105090487A (en) * | 2015-09-08 | 2015-11-25 | 梁稚子 | Internal rotor concave-convex friction driven adaptive automatic transmission driving assembly of electric motorcycle |
| CN105090484A (en) * | 2015-09-08 | 2015-11-25 | 西南大学 | Electric motorcycle inner rotor motor spiral taper sleeve driving self-adaption automatic transmission drive assembly |
| CN105090421A (en) * | 2015-09-08 | 2015-11-25 | 西南大学 | Bow cone type two-gear self-adaptation automatic variable speed driving assembly for external rotor motor of electric motorcycle |
| CN105090486A (en) * | 2015-09-08 | 2015-11-25 | 西南大学 | Outer rotor motor spiral type taper sleeve transmission self-adaptation automatic speed changing drive assembly of electric motor car |
| CN105370875A (en) * | 2015-09-08 | 2016-03-02 | 梁稚子 | Bow disc type two-gear self-adaptation automatic speed changing drive assembly of outer rotor motor of electric motorcycle |
| CN105114572A (en) * | 2015-09-08 | 2015-12-02 | 梁稚子 | Electric motorcycle external rotor motor biconical friction transmission self-adaptive automatic speed-changing drive assembly |
| CN105114615A (en) * | 2015-09-08 | 2015-12-02 | 梁稚子 | Electric motorcycle internal rotor motor biconical friction transmission self-adaptive automatic speed-changing drive assembly |
| CN105090485A (en) * | 2015-09-08 | 2015-11-25 | 西南大学 | Lateral hanging spiral type taper sleeve transmission self-adaptation automatic speed changing drive assembly of electric motor car |
| CN105370835A (en) * | 2015-09-08 | 2016-03-02 | 梁稚子 | Bow cone type two-gear self-adaptation automatic speed changing drive assembly of inner rotor motor of electric motorcycle |
| CN105156662A (en) * | 2015-09-08 | 2015-12-16 | 西南大学 | Waveform friction transmission self-adaption automatic speed change drive assembly of external rotor electric machine of electric motorcycle |
| CN105156617A (en) * | 2015-09-08 | 2015-12-16 | 梁稚子 | Concave-convex type friction drive side hanging type self-adaption automatic variable speed drive assembly of electric motor car |
| CN105156663A (en) * | 2015-09-08 | 2015-12-16 | 西南大学 | Inner rotor motor wave-shaped friction transmission self-adaption automatic variable speed drive assembly of electric motor car |
| CN105253245A (en) * | 2015-09-08 | 2016-01-20 | 梁稚子 | Electric motor car external rotor electric machine concave-convex friction drive self-adaption automatic transmission drive assembly |
| CN105129016A (en) * | 2015-09-09 | 2015-12-09 | 西南大学 | Side-hung bow cone swing type self-adaption automatic variable-speed drive assembly for electric motorcycle |
| CN105129016B (en) * | 2015-09-09 | 2018-09-04 | 西南大学 | Battery-operated motor cycle pendant bends conical pendulm formula self-adapting automatic gear shift drive assembly |
| CN105156618A (en) * | 2015-09-09 | 2015-12-16 | 西南大学 | External rotor motor cyrtoconic swing type self-adaption automatic variable speed drive assembly of electric motor car |
| CN105270562A (en) * | 2015-09-09 | 2016-01-27 | 梁稚子 | Side-hanging pendulum type self-adaptive automatic transmission driving assembly for electric motorcycle |
| CN105299217A (en) * | 2015-09-09 | 2016-02-03 | 西南大学 | Pendulum type self-adaption automatic variable speed drive assembly of electric motorcycle inner rotor motor bow cone |
| CN105156658A (en) * | 2015-09-09 | 2015-12-16 | 梁稚子 | Inner rotor motor swing type self-adaption automatic variable speed drive assembly of electric motor car |
| CN105221734A (en) * | 2015-09-09 | 2016-01-06 | 梁稚子 | Battery-operated motor cycle external rotor electric machine pendulum-type self-adapting automatic gear shift drives assembly |
| CN105114614A (en) * | 2015-09-21 | 2015-12-02 | 西南大学 | Spiral type triangular friction transmission self-adaptation automatic variable speed drive assembly of electric motorcycle |
| CN105711409A (en) * | 2016-01-27 | 2016-06-29 | 柳超 | Three-gear speed change wheel based on cam gear shifting |
| CN105711409B (en) * | 2016-01-27 | 2018-01-23 | 泰州市润杰五金机械制造有限公司 | A kind of three gear speed change wheels based on cam gearshift |
| CN110005801A (en) * | 2019-04-16 | 2019-07-12 | 西南大学 | Double mechanical shaft end output adaptive automatic transmission of overdrive clutch |
| CN110014829A (en) * | 2019-04-16 | 2019-07-16 | 西南大学 | Double mechanical shaft end output adaptive fluid drive power drive systems of overdrive clutch |
| CN110185790A (en) * | 2019-04-16 | 2019-08-30 | 西南大学 | Double mechanical axle sleeve output adaptive fluid drive power drive systems of overdrive clutch |
| WO2020211696A1 (en) * | 2019-04-16 | 2020-10-22 | 西南大学 | Dual-overrunning clutch shaft sleeve output adaptive automatic transmission main shaft assembly, gearbox, and drive system |
| CN110005801B (en) * | 2019-04-16 | 2020-12-04 | 西南大学 | Double-overrunning clutch mechanical shaft end output self-adaptive automatic transmission |
| CN110017369A (en) * | 2019-04-17 | 2019-07-16 | 西南大学 | Double overdrive clutch axle sleeve output adaptive automatic transmission of planetary gear train input |
| CN110017370A (en) * | 2019-04-18 | 2019-07-16 | 西南大学 | The mechanical double overdrive clutch self-adapting automatic gear shift main shaft assembly of planetary system output |
| CN110193572A (en) * | 2019-06-27 | 2019-09-03 | 马鞍山钢铁股份有限公司 | The manufacturing method of double S type web wheel press shaping die devices and double S type web wheels |
| CN110193572B (en) * | 2019-06-27 | 2024-04-09 | 马鞍山钢铁股份有限公司 | double-S-shaped radial plate wheel bending forming device and manufacturing method of double-S-shaped radial plate wheel |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102717705B (en) | 2015-07-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102717705A (en) | Mechanical intelligent adaptive double-gear automatic speed change hub with multiple cams | |
| CN102748450A (en) | Mechanical intelligent adaptive two-gear multi-cam automatic speed change driver | |
| CN102748449B (en) | Planetary intelligent self-adaptive two-gear multi-cam automatic speed change driver | |
| CN102720818A (en) | Mechanical, intelligent, adaptive, two-speed and multi-cam automatic transmission | |
| CN105151216B (en) | The spiral arcuate friction transmission self-adapting automatic gear shift drive assembly of battery-operated motor cycle | |
| CN101456439B (en) | Intelligent automatic speed changing hybrid power motorcycle | |
| CN102537265A (en) | Mechanical intelligent self-adaption two-gear automatic speed change driving assembly | |
| CN101525034B (en) | Double cam self-adapting automatic gear shifting hub | |
| CN105129016A (en) | Side-hung bow cone swing type self-adaption automatic variable-speed drive assembly for electric motorcycle | |
| CN105090484A (en) | Electric motorcycle inner rotor motor spiral taper sleeve driving self-adaption automatic transmission drive assembly | |
| CN105151215A (en) | Lateral-hung bow disk type two-gear self-adaption automatic speed change driving assembly for electric motorcycle | |
| CN102529572B (en) | Mechanical intelligent self-adaption two-gear automatic-gear-shifting hub | |
| CN101254745B (en) | Planetary conical plate type automatic transmission electric power driven hub | |
| CN101311018A (en) | Electrodynamic conical disk on-off cam self-adapting automatic gear shifting hub | |
| CN105253246A (en) | Spiral disc type friction transmission self-adaption automatic speed change drive assembly for electric motor car | |
| CN103438177A (en) | Multi-cam self-adaptive multi-gear automatic transmission | |
| CN102588548A (en) | Mechanical intelligent adaptive two-gear automatic transmission | |
| CN105270562A (en) | Side-hanging pendulum type self-adaptive automatic transmission driving assembly for electric motorcycle | |
| CN105156658B (en) | Battery-operated motor cycle inner rotor motor pendulum-type self-adapting automatic gear shift drive assembly | |
| CN101456348B (en) | Intellectualized two shift-gears automatic speed-changing electric wheel hub | |
| CN102734350B (en) | Mechanical intelligent self-adaptation automatic clutch | |
| CN102555789B (en) | Mechanical intelligent adaptive double-automatic speed changer driving assembly | |
| CN105216964A (en) | Battery-operated motor cycle waveform frictional transmission side hanging self-adapting automatic gear shift drives assembly | |
| CN105090421A (en) | Bow cone type two-gear self-adaptation automatic variable speed driving assembly for external rotor motor of electric motorcycle | |
| CN105172991A (en) | Bow disc type two-gear self-adaption automatic speed change drive assembly of inner rotor motor of electric motorcycle |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CP02 | Change in the address of a patent holder | ||
| CP02 | Change in the address of a patent holder |
Address after: 402460 Xueyuan Road 160, Rongchang District, Chongqing Patentee after: Southwest University Address before: 400715 No. 1 Tiansheng Road, Beibei District, Chongqing Patentee before: Southwest University |
|
| CP02 | Change in the address of a patent holder | ||
| CP02 | Change in the address of a patent holder |
Address after: 400715 No. 1, natural road, Beibei District, Chongqing Patentee after: SOUTHWEST University Address before: 402460 Rongchang District, Xueyuan Road, No. 160, Patentee before: SOUTHWEST University |