CN109838529A - Gear ring inputs planetary crankshaft cycloid differential mechanism - Google Patents

Abstract

Gear ring inputs planetary crankshaft cycloid differential mechanism, is made of planet carrier, at least two A type crankshafts, at least two A type crankshaft toothed wheels, at least two Type B crankshafts, at least two Type B crankshaft toothed wheels, at least one A type wobble gear, wheel for inputting A, at least one Type B wobble gear, output wheel B and at least one linkage gear；The rotation axle center of the planet carrier, wheel for inputting A and output wheel B is coaxial；The eccentricity of peer's eccentric shaft is identical on each A type crankshaft, and the phase of each A type crankshaft is identical, and each A type crankshaft is coaxial and circumferentially fixed with the rotation axle center of each A type crankshaft toothed wheel respectively；The eccentricity of peer's eccentric shaft is identical on each Type B crankshaft, and the phase of each Type B crankshaft is identical, and each Type B crankshaft is coaxial and circumferentially fixed with the rotation axle center of each Type B crankshaft toothed wheel respectively；The rotation axle center of all crankshafts is fixed on the planet carrier, the rotation axle center of all crankshafts and planet carrier rotation axis parallel.

Description

Gear ring inputs planetary crankshaft cycloid differential mechanism

Technical field

The present invention relates to a kind of differential mechanisms, belong to mechanical transmission component technical field, in particular to one kind can be used for automobile Gear ring input planetary crankshaft cycloid differential mechanism.

Background technique

Differential mechanism is a kind of mechanical transmission component, and the power transmission for being chiefly used in exporting automobile gearbox is to two or four Wheel is driven, the track for causing driving wheel to press through due to Uneven road and vehicle turning etc. is different, if keeping synchronized Rotation will result in the increased friction on wheel and road surface, increase vehicle travel resistance, so differential mechanism is needed according to each driving The different working orders of wheel export revolving speed to wheel, and traditional differential mechanism is mostly helical gear or crown gear structure.

Limited-slip differential, English entitled Limited Slip Differential, abbreviation LSD.Limited-slip differential cares for name Think justice be exactly limiting wheel slide a kind of modified differential mechanism, refer to driving wheel rotating speed difference be allowed in a certain range, with Guarantee the class differential mechanism of the driving performances such as normal turning, but when a certain driving wheel skid or it is hanging when can limit differential mechanism not again By whole power outputs to skidding or hanging wheel, facilitates vehicle and get rid of poverty and manipulation when fierce drive, for example work as vehicle As soon as wheel is fallen into pit-hole, this wheel, which has no any frictional force, to be sayed, the wheel that lands but has great resistance relatively, general at this time The effect of logical differential mechanism can allow all dynamic feedbacks to the wheel of low friction.Fall into pit-hole wheel can not stall it is dynamic, and Complete attonity, such vehicle can not just travel land wheel instead, at this moment if vehicle assembly is that limited-slip differential would not go out Existing such case.Current limited-slip differential, which has using automatically controlled multiplate clutch, realizes locking, but reaction speed is relatively Slowly, also have through the worm and gear of Purely mechanical and realize, cost is relatively high, also inconvenient when as center differential Scores are not waited to match in the output torque of setting front and back wheel.

Summary of the invention

The invention proposes gear rings to input planetary crankshaft cycloid differential mechanism, and specific technical solution is as follows.

Gear ring inputs planetary crankshaft cycloid differential mechanism, by planet carrier, at least two A type crankshafts, at least two A type crank teeths Wheel, at least two Type B crankshafts, at least two Type B crankshaft toothed wheels, at least one A type wobble gear, wheel for inputting A, at least one B Type wobble gear, output wheel B and at least one linkage gear composition；The axis of rotation of the planet carrier, wheel for inputting A and output wheel B The heart is coaxial；The eccentricity of peer's eccentric shaft is identical on each A type crankshaft, and the phase of each A type crankshaft is identical, each A type crankshaft It is coaxial and circumferentially fixed with the rotation axle center of each A type crankshaft toothed wheel respectively；The eccentricity of peer's eccentric shaft on each Type B crankshaft Identical, the phase of each Type B crankshaft is identical, and each Type B crankshaft is coaxial and all with the rotation axle center of each Type B crankshaft toothed wheel respectively To fixation；The rotation axle center of all crankshafts is fixed on the planet carrier, and the rotation axle center and planet carrier rotation axle center of all crankshafts are flat Row；Eccentric shafts at different levels on each A type crankshaft are radially fixed with A type wobble gear at the same level respectively, at different levels on each Type B crankshaft Eccentric shaft is radially fixed with Type B wobble gear at the same level respectively；Wheel for inputting A includes ring gear, and the ring gear and each A type are swung Gear engagement composition internal gear pair, output wheel B includes ring gear, which engages with each Type B wobble gear in composition Gear pair；Each A type crankshaft toothed wheel is at least engaged with a Type B crankshaft toothed wheel with the same linkage gear；Each Type B crank teeth Wheel is at least engaged with an A type crankshaft toothed wheel with the same linkage gear；The biography of all A type crankshaft toothed wheels and Type B crankshaft toothed wheel It moves than identical.The transmission ratio that the transmission ratio absolute value of the linkage gear and wheel for inputting A are greater than linkage gear and output wheel B is absolute Value；Planet carrier, wheel for inputting A and output wheel B are respectively provided with and the tooth-shape structure of differential mechanism external world part transmitting torque or hole Shape structure.The usual state of torque of gear ring input planetary crankshaft cycloid differential mechanism of the invention is inputted by wheel for inputting A, from planet Frame and output wheel B output；Relative to planet carrier, from circling, to drive output wheel B relative to planet carrier rotation be more than one to wheel for inputting A It just can guarantee that output wheel B and planet carrier can only be round about by certain rotating ratio rotations relative to wheel for inputting A in this way in week, this By A type wobble gear and Type B wobble gear respectively with the engaging tooth ratio of corresponding ring gear on wheel for inputting A and output wheel B and A What type crankshaft toothed wheel and Type B crankshaft toothed wheel were determined with the gear ratio of linkage gear respectively, so the linkage gear and wheel for inputting A Transmission ratio absolute value be greater than linkage gear and output wheel B transmission ratio absolute value, A type crankshaft and the transmission ratio of wheel for inputting A are The rotating ratio of the cycloid gear revolution and ring gear rotation of few teeth difference cycloidal gear transmission, the transmission ratio of Type B crankshaft and wheel for inputting B For the rotating ratio of the cycloid gear revolution and ring gear rotation of few teeth difference cycloidal gear transmission, the biography of linkage gear and wheel for inputting A The product of the transmission ratio of dynamic transmission ratio and A type crankshaft and wheel for inputting A than being equal to linkage gear and A type crankshaft toothed wheel, link tooth The transmission ratio of wheel and output wheel B are equal to the transmission of the transmission ratio and Type B crankshaft and output wheel B of linkage gear and Type B crankshaft toothed wheel The product of ratio；The purpose of structure of the invention is the differential output in order to realize revolving speed, and differential exports situation and planet carrier and output It is related that the resistance of wheel B turns loading condition, since being that differential gear its essence also can be achieved on torque from planet carrier, defeated certainly Enter to take turns A and output wheel B any one or two at input, then never input output mechanical transmission mechanism；Although one The function of differential mechanism also may be implemented in a A type wobble gear, but its mechanical balance is not good enough, when using multiple A type wobble gears Shi Suoyou A type wobble gear on wheel for inputting A gear ring composition gear pair tooth than identical, when use multiple Type B wobble gears Shi Suoyou Type B wobble gear is with the gear pair tooth of the gear ring composition on output wheel B than identical；A type crankshaft, which is equipped with, swings tooth with A type The identical crank throw of number is taken turns, Type B crankshaft is equipped with crank throw identical with Type B wobble gear number；A type wobble gear is limited to rotation shaft At least two A type crankshafts being fixed on the planet carrier can only revolve relative to planet carrier, between the ring gear on wheel for inputting A Tooth ratio determine wheel for inputting A relative to planet carrier rotation certain angle A type wobble gear relative to planet carrier to the same direction Revolution angle, the revolution angle of A type wobble gear and direction are equal to the rotation angle and direction of A type crankshaft；Type B wobble gear Being limited at least two Type B crankshafts that rotation shaft is fixed on the planet carrier can only revolve relative to planet carrier, with output wheel B On ring gear between tooth ratio determine output wheel B relative to planet carrier rotation certain angle Type B wobble gear relative to row For carrier to the revolution angle of the same direction, the revolution angle of Type B wobble gear and direction are equal to rotation angle and the side of Type B crankshaft To；The A type crankshaft and Type B crankshaft engage realization by A type crankshaft toothed wheel and Type B crankshaft toothed wheel with linkage gear simultaneously and join It is dynamic, so that wheel for inputting A and output wheel B can only be rotated relative to planet carrier to the same direction, and its rotation relative to planet carrier Angle ratio is fixed, and limits wheel for inputting A and output wheel B relative to the rotational angle ratio of planet carrier less than 1, planet carrier and output wheel B can only be rotated round about relative to wheel for inputting A with certain rotating ratio；The gear or gear ring can be by pin wheel housing and needle The pinwheel of tooth composition, the needle tooth can also include pin gear sleeve, and the pin shaft also may include axle sleeve, and crank throw refers to the one of crankshaft Grade eccentric shaft, can directly be processed on trunnion when rod journal is thicker eccentric shaft omit crank, can also by Circumferential fixed eccentric shaft set is realized on trunnion, may include bearing or axle sleeve on the axle journal of crankshaft；The planet carrier of differential mechanism is logical It crosses tooth or hole and extraneous part transmits torque, planet carrier usually passes through the tooth of circumferential surface when as center differential and front-wheel passes Moving axis engagement is linked by chain and front axle differential transmission shaft, and wheel for inputting A passes through on tooth-shape structure and output shaft of gear-box Tooth engagement or dental inlay connect input torque, the tooth-shape structure that output wheel B usually passes through circumferential surface forms spline and rear axle differential Device is driven axis connection；The part or component of above-mentioned composition gear ring input planetary crankshaft cycloid differential mechanism can be selected and be integrally machined into The part of type or the component integrally moved, wherein crankshaft with and its circumferentially fixed crankshaft toothed wheel can process integrally fixation Part.

The differential mechanism further includes housing part.One in the housing part and planet carrier, wheel for inputting A and output wheel B It is a circumferentially fixed, can also partial shell part directly be processed on planet carrier or wheel for inputting A or output wheel B；In wheel for inputting A When not limiting fixed by extraneous part axial with output wheel B, the shell structure will have axis to differential mechanism inner body To limit, the axial limiting guarantees axial component power that differential mechanism inner body is generated when transmitting torque by helical gear to axis To inside support force when two side compressions.

The A type crankshaft toothed wheel or Type B crankshaft toothed wheel are helical gear.The linkage gear and A type crankshaft toothed wheel or Type B are bent Shaft gear meshed gears is also helical gear, and helical gear pair can produce the stress of axial component, the stress when transmitting torque The frictional force between the other parts of the frictional force or increasing gear axial compression between gear can be increased, to increase gear and its The rotary resistance of his rotational parts, this rotary resistance will form the differential gearing resistance of differential mechanism, generate the sliding effect of differential mechanism limit Fruit.

The gear ring input planetary crankshaft cycloid differential mechanism includes two A type wobble gears, and A type crankshaft is inclined with two-stage Mandrel and two-stage eccentric shaft phase phase difference 180 degree, the two-stage eccentric shaft of A type crankshaft are each passed through the phase of two A type wobble gears Answer axis hole and two A type wobble gears radially fixed, wheel for inputting A includes engaging composition with two A type wobble gears respectively simultaneously The ring gear of internal gear pair, the identical number of teeth of two A type wobble gear flank profils are equal；The gear ring input planetary crankshaft cycloid is poor Fast device includes two Type B wobble gears, and Type B crankshaft has two-stage eccentric shaft and two-stage eccentric shaft phase phase difference 180 degree, and Type B is bent The two-stage eccentric shaft of axis be each passed through two Type B wobble gears corresponding axis hole and two Type B wobble gears it is radially fixed, output Wheel B includes the ring gear for engaging composition internal gear pair with two Type B wobble gears respectively simultaneously, two Type B wobble gear flank profils The identical number of teeth is equal.Although the function of differential mechanism also may be implemented in an A type wobble gear, its mechanical balance is not good enough；More Can preferably to select two A type wobble gears and the A type crankshaft of at least two two-stage crank throw phase phase difference 180 degrees to cooperate, Two Type B wobble gears and the cooperation of the Type B crankshaft of at least two two-stage crank throw phase phase difference 180 degrees are selected simultaneously；On crankshaft The revolution phase phase difference 180 degree for two wobble gears that two-stage eccentric shaft phase phase difference 180 degree causes it to pass through, the two swings The phase difference of 180 degree ensure that the two wobble gears are radially pressed caused by ring gear when gear is engaged with the same ring gear Power is offset, the two wobble gears also assure that its revolution with respect to differential mechanism rotation axle center will not influence differential mechanism entirety simultaneously The center of gravity of rotation.

At least a piece of friction plate is additionally provided in the differential mechanism.Friction plate can select the higher material of coefficient of friction or table Face technique is made, and the friction plate can be added between wobble gear and other parts, can also be added in A type crankshaft toothed wheel or B Between type crankshaft toothed wheel and other parts, frictional resistance in order to further increase, friction plate can by internal tooth or external tooth with it is defeated Enter to take turns A or output wheel B is circumferentially fixed, friction plate can also be circumferentially fixed by internal tooth or external tooth and planet carrier, and will be with difference The interspersed setting of the circumferentially fixed multi-plate friction plate of the part of rotary state.

The differential mechanism is equipped with shaft coupling between A type crankshaft and A type crankshaft toothed wheel or Type B crankshaft and Type B crankshaft toothed wheel, The shaft coupling can produce the power of axial component when transmitting torque.The connection of torque is transmitted between A type crankshaft and Type B crankshaft The power of axial component is generated when shaft coupling being set on dynamic path, and transmitting torque by shaft coupling, and with the power of this axial component Moving parts when compressing from differential mechanism differential gearing to both sides generate and limit sliding effect, can thus realize without using helical gear The sliding effect of the limit of differential mechanism.

The shaft coupling is the jaw and toothed coupling of the contact surface comprising pressure angle greater than 0 degree.The jaw and toothed coupling Form include end face jaw and toothed coupling, circumferential surface jaw and toothed coupling and conical surface jaw and toothed coupling, the castellated shaft coupling Device includes at least coupler component part A and coupler component part B, and the coupler component part A and coupler component part B are made by the convex-concave Mutually circumferentially the transmitting of castellated torque is realized in limit to type structure, and the circumferential surface jaw and toothed coupling can be understood as external gear and same The ring gear of the number of teeth is nested, in order to realize that coupler component part A and coupler component part B described in the sliding effect of limit can be when transmitting torque Axial component stress under it is a small amount of mobile to axial；The coupler component part and crankshaft or crankshaft toothed wheel can be one The part of processing or the component integrally moved.

The shaft coupling is ball ramp or sliding block ramp-type shaft coupling；The shaft coupling is with ball ramp or sliding block The shaft coupling of ramp linkage mechanism, ball ramp or sliding block ramp linkage mechanism are by ball or sliding block in torque transfer components The transmission mechanism limited to realize the component that can produce axial force while torque transmitting in the groove of both ends, essence is to pass through Side with can the part of groove of accommodating portion ball or sliding block deliver torque to ball or sliding block, then ball or sliding block Transfer torque to the other side with can accommodating portion ball or sliding block groove part, use ball ramp or sliding block ramp Mechanism transmitting torque benefit be part it is easy to process go out setting pressure angle.

Gear ring input planetary crankshaft cycloid differential mechanism of the invention can be by setting A type wobble gear and wheel for inputting A The tooth of ring gear realizes the distribution of torque output than the difference of the tooth ratio with the ring gear on Type B wobble gear and output wheel B Trend difference can also compare difference with linkage gear meshed gears respectively by adjusting A type crankshaft toothed wheel and Type B crankshaft toothed wheel Come realize torque output distribution trend difference, this is an important advance advantage of differential mechanism of the invention, by setting on The gear ratio for stating adjustable output torque distribution trend solves the range that various differential mechanisms in the prior art adjust torque distribution Limitation also reduces difficulty of processing and be processed into that differential mechanism is the moulding for adjusting torque distribution and designing compared with prior art This, certain differential mechanisms compared with the prior art more improve the torque carrying capability under same size, reduce in other words identical Differential mechanism volume under load-carrying ability, the rotary inertia for reducing transmission mechanism can effectively promote transmission efficiency.

Gear ring input planetary crankshaft cycloid differential mechanism of the invention is mainly used for the engine power of vehicle by gearbox Backward wheel output, when as center differential, usually gearbox outputs torque to wheel for inputting A, planet carrier and output Wheel B, which is respectively exported torque by transmission shaft, gives antero posterior axis differential mechanism.

Detailed description of the invention

The gear ring of Fig. 1 embodiment 1 inputs planetary crankshaft cycloid differential design schematic diagram 1(cross-sectional view).

The gear ring of Fig. 2 embodiment 1 inputs 2 cross-sectional view of planetary crankshaft cycloid differential design schematic diagram).

The gear ring of Fig. 3 embodiment 1 inputs planetary crankshaft cycloid differential design schematic diagram 3(cross-sectional view).

The gear ring of Fig. 4 embodiment 1 inputs planetary crankshaft cycloid differential design schematic diagram 4(cross-sectional view).

The gear ring of Fig. 5 embodiment 1 inputs planetary crankshaft cycloid differential design schematic diagram 5(cross-sectional view).

The gear ring of Fig. 6 embodiment 1 inputs planetary crankshaft cycloid differential design schematic diagram 6(cross-sectional view).

The gear ring of Fig. 7 embodiment 1 inputs planetary crankshaft cycloid differential mechanism part explosive view.

The gear ring of Fig. 8 embodiment 1 inputs planetary crankshaft cycloid differential mechanism perspective view.

In figure: 1, shell；2, wheel for inputting A；3, output wheel B；4, A type wobble gears；5, Type B wobble gear；6, A types are bent Shaft gear；The excentric sleeve of 7, A type crankshafts；8, Type B crankshaft toothed wheel；9, the excentric sleeve of Type B crankshaft, 10, linkage gear；11, Planet carrier.

Specific embodiment

Embodiment 1, as shown in Fig. 1 ~ Fig. 8, gear ring inputs planetary crankshaft cycloid differential mechanism, bent by planet carrier, two A types Axis, two A type crankshaft toothed wheels, two Type B crankshafts, two Type B crankshaft toothed wheels, two A type wobble gears, wheel for inputting A, two B Type wobble gear, output wheel B, linkage gear and shell composition；The rotation of the wheel for inputting A, output wheel B, planet carrier and shell Axle center is coaxial, and A type crankshaft and Type B crankshaft are all to be separately fixed at the A type crankshaft toothed wheel axis of rotation and B by spline by excentric sleeve It is realized on the axis of rotation of type crankshaft toothed wheel, also ensure that the coaxial and circumferentially fixed of crankshaft and corresponding crankshaft toothed wheel simultaneously；A type Crankshaft toothed wheel, Type B crankshaft toothed wheel and linkage gear all select the involute external tooth spur gear of identical modulus, A type crankshaft toothed wheel and B Type crankshaft toothed wheel is engaged with linkage gear respectively simultaneously；, the planet carrier is made of two panels, two panels planet carrier by external splines with Shell is circumferentially fixed；A type crankshaft has two-stage crank throw and two-stage crank throw phase phase difference 180 degree, the two-stage crank throw of each A type crankshaft It is each passed through the corresponding axis hole of two A type wobble gears, be machined on wheel for inputting A while being engaged with two A type wobble gears Ring gear, equal two A type wobble gear numbers of teeth are all 15 teeth, and the gear ring engaged on wheel for inputting A with A type wobble gear is 16 Tooth；Type B crankshaft is with two-stage crank throw and two-stage crank throw phase phase difference 180 degree, the two-stage crank throw of Type B crankshaft are each passed through two B The corresponding axis hole of type wobble gear, the ring gear for being machined with while being engaged with two Type B wobble gears on output wheel B, two Type Bs The equal wobble gear number of teeth is all 11 teeth, and the ring gear engaged on output wheel B with Type B wobble gear is 12 teeth；Shell is machined with Tooth-shape structure is used to link with front axle differential transmission shaft, and wheel for inputting A is equipped with internal spline for connecting output shaft of gear-box, exports Wheel B is equipped with internal spline for connecting rear axle differential transmission shaft；The present embodiment wobble gear and the gear ring being meshed therewith all select With round cycloidal profile, part selects chrome-molybdenum steel to be process for material in the present embodiment.

Claims (8)

1. gear ring inputs planetary crankshaft cycloid differential mechanism, it is characterized in that: by planet carrier, at least two A type crankshafts, at least two A Type crankshaft toothed wheel, at least two Type B crankshafts, at least two Type B crankshaft toothed wheels, at least one A type wobble gear, wheel for inputting A, extremely A few Type B wobble gear, output wheel B and at least one linkage gear composition；The planet carrier, wheel for inputting A and output wheel B Rotation axle center is coaxial；The eccentricity of peer's eccentric shaft is identical on each A type crankshaft, and the phase of each A type crankshaft is identical, each A Type crankshaft is coaxial and circumferentially fixed with the rotation axle center of each A type crankshaft toothed wheel respectively；Peer's eccentric shaft on each Type B crankshaft Eccentricity is identical, and the phase of each Type B crankshaft is identical, and each Type B crankshaft is same with the rotation axle center of each Type B crankshaft toothed wheel respectively Axis is simultaneously circumferentially fixed；The rotation axle center of all crankshafts is fixed on the planet carrier, the rotation axle center of all crankshafts and planet carrier rotation Axis parallel；Eccentric shafts at different levels on each A type crankshaft are radially fixed with A type wobble gear at the same level respectively, on each Type B crankshaft Eccentric shafts at different levels it is radially fixed with Type B wobble gear at the same level respectively；Wheel for inputting A includes ring gear, the ring gear and each A Type wobble gear engagement composition internal gear pair, output wheel B includes ring gear, which engages with each Type B wobble gear Form internal gear pair；Each A type crankshaft toothed wheel is at least engaged with a Type B crankshaft toothed wheel with the same linkage gear；Each Type B Crankshaft toothed wheel is at least engaged with an A type crankshaft toothed wheel with the same linkage gear；All A type crankshaft toothed wheels and Type B crank teeth The transmission ratio of wheel is identical；The transmission ratio absolute value of the linkage gear and wheel for inputting A are greater than the transmission of linkage gear and output wheel B Compare absolute value；Planet carrier, wheel for inputting A and output wheel B are respectively provided with the tooth form knot with differential mechanism external world part transmitting torque Structure or hole shape structure.

2. gear ring according to claim 1 inputs planetary crankshaft cycloid differential mechanism, it is characterized in that: the differential mechanism further includes Housing part.

3. gear ring according to claim 1 inputs planetary crankshaft cycloid differential mechanism, it is characterized in that: the A type crankshaft toothed wheel Or Type B crankshaft toothed wheel is helical gear.

4. gear ring according to claim 1 inputs planetary crankshaft cycloid differential mechanism, it is characterized in that: the gear ring line of input Star crankshaft cycloid differential mechanism includes two A type wobble gears, and A type crankshaft has two-stage eccentric shaft and two-stage eccentric shaft phase phase difference 180 degree, the two-stage eccentric shaft of A type crankshaft are each passed through the corresponding axis hole and two A type wobble gear diameters of two A type wobble gears To fixation, wheel for inputting A includes the ring gear for engaging composition internal gear pair with two A type wobble gears respectively simultaneously, two A type pendulum The identical number of teeth of movable tooth tooth profile is equal；The gear ring input planetary crankshaft cycloid differential mechanism includes two Type B wobble gears, B Type crankshaft is with two-stage eccentric shaft and two-stage eccentric shaft phase phase difference 180 degree, the two-stage eccentric shaft of Type B crankshaft are each passed through two The corresponding axis hole of Type B wobble gear and two Type B wobble gears are radially fixed, and output wheel B includes putting respectively with two Type Bs simultaneously The ring gear of moving gear engagement composition internal gear pair, the identical number of teeth of two Type B wobble gear flank profils are equal.

5. gear ring according to claim 1 inputs planetary crankshaft cycloid differential mechanism, it is characterized in that: also setting in the differential mechanism There is at least a piece of friction plate.

6. gear ring according to claim 1 inputs planetary crankshaft cycloid differential mechanism, it is characterized in that: the differential mechanism is in A type Shaft coupling is equipped between crankshaft and A type crankshaft toothed wheel or Type B crankshaft and Type B crankshaft toothed wheel, the shaft coupling is when transmitting torque It can produce the power of axial component.

7. gear ring according to claim 6 inputs planetary crankshaft cycloid differential mechanism, it is characterized in that: the shaft coupling be comprising The jaw and toothed coupling of contact surface of the pressure angle greater than 0 degree.

8. gear ring according to claim 6 inputs planetary crankshaft cycloid differential mechanism, it is characterized in that: the shaft coupling is ball Ramp or sliding block ramp-type shaft coupling.