CN106801736A - A kind of differential mechanism - Google Patents
A kind of differential mechanism Download PDFInfo
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- CN106801736A CN106801736A CN201710215093.3A CN201710215093A CN106801736A CN 106801736 A CN106801736 A CN 106801736A CN 201710215093 A CN201710215093 A CN 201710215093A CN 106801736 A CN106801736 A CN 106801736A
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- gear
- idler
- type
- housing
- output
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
Abstract
The present invention relates to a kind of differential mechanism, more particularly to a kind of to can be used for the differential mechanism of automobile, internal gear pair that internal gear pair, wobble gear B and the output gear B being made up of housing, wobble gear A and output gear A are constituted, at least two A types idler gears, at least two Type B idler gears are constituted；The radial direction of each A type idler gear is fixed and rotation axis and housing rotation diameter parallel with housing, each A types idler gear is at least engaged with a Type B idler gear, and each is identical with the gear pair gear ratio that Type B idler gear is constituted by A types idler gear, each A type idler gear is provided with the eccentric shaft of axis and its rotation diameter parallel, the eccentric shaft opposed gear axis of rotation on each A type idler gear is apart from identical, eccentric shaft phase on all A types idler gears is identical, eccentric shaft radial on each A type idler gear is fixed with wobble gear A respectively, output gear A is coaxial with housing rotation rotating shaft.
Description
Technical field
It is more particularly to a kind of to can be used for the differential mechanism of automobile the present invention relates to a kind of differential mechanism, belong to mechanical transmission component
Technical field.
Background technology
Differential mechanism is a kind of mechanical transmission component, is used for the power transmission for exporting automobile gearbox to two or four
Driving moment, because the reasons such as Uneven road and turn inside diameter cause the track that driving moment is pressed through different, if keeping synchronized
Rotation will result in wheel and increase with the friction on road surface, increase vehicle travel resistance, so differential mechanism is needed according to each driving
To wheel output speed, traditional differential mechanism is generally helical gear or crown gear structure to the different working orders of wheel.
Limited-slip differential, English entitled Limited Slip Differential, abbreviation LSD.Limited-slip differential, turns round and look at name
Think justice be exactly limiting wheel slip a kind of modified differential mechanism, refer to driving wheel rotating speed difference be allowed within the specific limits, with
Ensure the class differential mechanism of the normal driving performance such as turn, 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, vehicle is contributed to get rid of poverty and fierce manipulation when driving.For example work as vehicle
One wheel is fallen into pit-hole, and this wheel just has no any frictional force can be sayed, the wheel that lands but has great resistance relatively, now general
The effect of logical differential mechanism can allow all dynamic feedbacks to the wheel of low friction.Fall into the wheel of pit-hole can not stall it is dynamic, and
Land wheel complete attonity on the contrary, such wheel cannot just be travelled, if at this moment vehicle assembling is that limited-slip differential would not go out
Existing such case.Current limited-slip differential has using automatically controlled multiplate clutch to realize locking, but reaction speed is relatively
Slowly, also have by the worm and gear of Purely mechanical come what is realized, cost is of a relatively high, it is also inconvenient during as center differential
In the output torque distribution of setting front and back wheel.
The content of the invention
In order to solve the above problems, the present invention proposes a kind of differential mechanism, and concrete technical scheme is as follows.
A kind of differential mechanism, the internal gear pair being made up of housing, wobble gear A and output gear A, wobble gear B and output
The internal gear pair of gear B composition, at least two A types idler gears, at least two Type B idler gears composition；Each A type center tooth
The radial direction of wheel is fixed and rotation axis and housing rotation diameter parallel with housing, each A types idler gear at least with a Type B
Idler gear is engaged, and each is identical with the gear pair gear ratio that Type B idler gear is constituted by A types idler gear, in each A type
Between gear be provided with the eccentric shaft of axis and its rotation diameter parallel, the eccentric shaft opposed gear on each A type idler gear from
Apart from identical, the eccentric shaft phase on all A types idler gears is identical, the eccentric shaft radial on each A type idler gear for rotating shaft
Fixed with wobble gear A respectively, output gear A is coaxial with housing rotation rotating shaft；The radial direction of each Type B idler gear is solid with housing
Fixed and rotation axis and housing rotation diameter parallel, each Type B idler gear are at least engaged with an A type idler gear, often
Individual Type B idler gear is provided with the eccentric shaft of axis and its rotation diameter parallel, and the eccentric shaft on each Type B idler gear is relative
Apart from identical, the eccentric shaft phase on all Type B idler gears is identical, the eccentric shaft on each Type B idler gear for its axis of rotation
Radially fixed with wobble gear B respectively, output gear B is coaxial with housing rotation rotating shaft.What above-mentioned spatial relation was limited retouches
State is a kind of more rigorous description method for limiting direct or indirect connection and contact between part, this area general technology
Personnel can understand the whole of annexation between part and technical solution of the present invention according to the description of above-mentioned spatial relation
Body structure；Housing can be the component that a part can also be made up of multiple parts, and the housing member is not necessarily intended to
Fully wrapped around all parts, it is only necessary to make above-mentioned part meet spatial relation and mechanics annexation；A type idler gears
It is exactly the rotation of each idler gear relative to the explanation of the radially fixed spatial relationship more precisely of housing with Type B idler gear
Axis is all fixed on by a point on housing radial section, or because to have between idler gear and housing bearing or
Person's oil lubrication needs to leave gap rotation axis to rotation and is limited in fixed area by very little on a housing radial section
In domain, housing and the relation of all idler gears can be understood as planet carrier and planetary relation, wobble gear A and all
Radially fixed relation between the eccentric shaft of A type idler gears also complies with foregoing description, wobble gear B and all Type B center tooths
Radially fixed relation between the eccentric shaft of wheel also complies with foregoing description；A types idler gear and Type B idler gear can be same
Gear, or the number of teeth it is different but the gear of external tooth wheel set can be constituted;Bias on above-mentioned all A types idler gears
Axle phase identical spatial relation can be understood as the bias of each A type idler gear of any two A type idler gears
The plane that the axial line of axle determines with gear rotation axial line remains parallel;Wobble gear A is with the housing axis of rotation during differential
Line is axle revolution synchronous with the rotation of each A type idler gear, during wobble gear B is with housing rotation axis as axle and each Type B
Between gear rotation synchronously revolve round the sun, differential mechanism operate when moment of torsion from housing be input into, it is defeated from output gear A and output gear B respectively
Go out, which kind of structure output is external force be input into further through and need not be included in the technical scheme of differential mechanism by which kind of structure, but
What typically usual gear or rotating shaft were exported, gear can have been reprocessed on the part or component of differential mechanism or connection has been machined with
The spline of axle.
Above-mentioned differential mechanism, housing is driven each A types idler gear and each Type B idler gear with shell by external force rotation
Body revolves round the sun around the housing axis of rotation, and the eccentric shaft on each A type idler gear drives wobble gear A with housing into rotation, wobble gear A
Output gear A is driven to rotate, the eccentric shaft on each Type B idler gear drives wobble gear B with housing into rotation, wobble gear B
Output gear B is driven to rotate, output gear A and output gear B export rotation respectively；When output gear A and output gear B rotating speeds
All parts are motionless with respect to housing stationary in differential mechanism when identical；Made when output gear A is different with the output loading of output gear B
Into rotating speed it is different when, output gear A and output gear B relatively rotate, both output gear A and output gear B respectively with shell
There is relative rotation in opposite direction in body, cause wobble gear A and wobble gear B all to occur relative to the housing axis of rotation with housing
The revolution in opposite direction of line, wobble gear A and wobble gear B are driven relative to the revolution of housing rotation axis by eccentric shaft
Each A types idler gear and each Type B idler gear rotation round about, are limited to A types idler gear and Type B idler gear
Engagement, output gear A and output gear B can only with a fixed rotating ratio relation relative to housing occur it is in opposite direction
Rotate against.Above-mentioned is the transitive relation transitive relation of moment of torsion and the differential output in other words of differential mechanism rotational motion of the invention
Realization principle；Differential mechanism of the invention is explained further potentially limiting the realization principle of sliding mechanism is:Output gear A and swing
The number of teeth of gear A determine wobble gear A that output gear A driven with respect to housing rotation with housing rotation axis be axle relative to shell
The rotating ratio of body revolution housing rotation relative with output gear A, revolution rotating speed and each A type idler gear of wobble gear A
Rotation rotating speed is identical, and the number of teeth of output gear B and wobble gear B determines output gear B with respect to the swing tooth that housing rotation drives
Rotating ratios of the wheel B with housing rotation axis as axle housing rotation relative with output gear B relative to housing revolution, wobble gear B
Revolution rotating speed it is identical with the rotation rotating speed of each Type B idler gear, when the two rotating ratios are higher, due to frictional force and profit
Differential mechanism internal load when rotating against of the presence of lubricating oil fluid resistance, output gear A and output gear B can be according to relative
The proportional amplification of rotary rpm, while this differential mechanism internal load is also causing between output gear A and wobble gear A and defeated
What is gone out between gear B and wobble gear B engages surface pressure increase, causes between output gear A and wobble gear A and output gear
Gear auxiliary driving resistance increase between B and wobble gear B, further increases the negative of output gear A and output gear B relative rotations
Carry, the increase of these loads all causes the extraneous output loading difference of output gear A and output gear B speed differences in balance,
Output gear A and output gear B is tended to synchronized output, that is, play the sliding effect of limit；Lock can be specifically realized when skidding
It is fixed, depending on the maximum that differential mechanism internal load increases, in theory when output gear A and output gear B opposing torque or
The differential mechanism internal load that relative rotation speed is caused can realize output gear A and output when being more than or equal to the moment of torsion for being input to housing
Relative locking between gear B.
The gear pair of above-mentioned wobble gear A and output gear A compositions or the gear of wobble gear B and output gear B compositions
Pair is cycloid tooth wheel set.Cycloid tooth wheel set includes cycloidal-pin wheel gear pair, when the less tooth difference of cycloid tooth wheel set, two gear phases
To the weekly assembly of rotation one one gear of correspondence around the rotation axial line revolution week more of another gear, resistance during rotation can be amplified
Power, and cycloid gear can select the less gear of the number of teeth, gear endurance be increased in limited space, additionally by tune
The tooth form of whole cycloid gear can also adjust the relation between the rotary resistance of gear engagement and torque loads, be more beneficial for implementing
Go out the differential mechanism of the different sliding abilities of limit.
Above-mentioned a kind of differential mechanism, it is characterized in that including at least 3 A types idler gears and at least 3 Type B idler gears.3
Individual above A types idler gear and more than 3 Type B idler gears just have 3 eccentric shafts to be connected with wobble gear A and wobble gear B,
The stability that wobble gear revolves round the sun around housing rotation axial line is more beneficial for, 3 eccentric shafts are more favorable to housing and rotarily drive
The torque load ability of wobble gear and housing synchronous rotary.
Above-mentioned output gear A and output gear B is external tooth gear.At this moment the rotation of output gear drives the pendulum in gear pair
Moving gear revolves round the sun to the direction opposite with output gear sense of rotation, and this is the gear drive between output gear and wobble gear
Resistance is bigger, is more beneficial for being applied to limited-slip differential, or cause rotary resistance after driving torque increases to certain fixed value
More than input torque, gear is caused to lock the effect for realizing differential lock.
Above-mentioned output gear A and output gear B is internal-gear.At this moment the rotation of output gear drives the pendulum in gear pair
Moving gear revolves round the sun to output gear sense of rotation identical direction, the at this moment gear drive between output gear and wobble gear
Resistance is smaller, is more beneficial for reducing resistance and loss of torque when differential mechanism differential is exported.
Above-mentioned A types idler gear and Type B idler gear are helical gear or worm screw.Bevel gear set into gear pair relative
Axial stress can be produced during rotation, this axial stress is conducive to increasing the friction pressure of gear and axial other parts,
Exactly increase the rotation resistance of gear；Worm screw belongs to a kind of gear, and the gear pair that worm screw and worm screw constitute is produced when rotating against
Raw axial stress, the frictional force in this axial stress increase worm tooth wheel set between worm screw and worm screw, increases worm screw rotation resistance
Power, while this axial stress is conducive to increasing the friction pressure of worm screw and axial other parts, also increases the rotation resistance of worm screw
Power；The engagement rotation of idler gear A and idler gear B can be caused after the resistance of idler gear rotation increases to certain fixed value
Resistance exceedes the moment of torsion for causing idler gear A and idler gear B to relatively rotate, and realizes the locking of differential mechanism.
Above-mentioned output gear A, output gear B, wobble gear A and wobble gear B are respectively relative to housing axial restraint.Phase
Be explained further for the spatial relationship of housing axial restraint be exactly with shell space position relationship along housing axial direction component
Keep constant, or because to there are bearing or oil lubrication needs to stay between the radial direction or circumferential movement and housing that need relative housing
There is gap, a relatively small fixed model is limited in along the component of housing axial direction in rotational parts and shell space position relationship
Also a kind of fixed form at last in enclosing, than as it is shown in the figures, housing limits output gear A's and output gear B from two ends
Away from the axial movement of housing, space occupy-place of the other parts in housing again limits output gear A and output gear B to shell
The movement at body center, wobble gear A and wobble gear B similarly, no matter which kind of axial restraint mode will retain other directions can
Influenceed to have certain gap by technique with mobile, but it can be to mend that " fixation " one word is used on the location expression in space
Fill what explanation technical scheme understood for persons skilled in the art, as long as because meeting present invention first paragraph
The technical scheme of description and all parts being axially unlikely to be endless, just must gear be limited in one it is a certain amount of
Move to axial in the range of, the connection of described spatial relation could be met, this limitation is the first segment description
Technical scheme further adds to be fixed as limitation as the implicit restriction of necessary and sufficient condition in the technical scheme of this section
Condition.
Above-mentioned A types idler gear and Type B idler gear are axially fixed relative to housing.Relative to housing axial restraint
It is exactly to keep constant along the component of housing axial direction with shell space position relationship that spatial relationship is explained further, or because needing
Need to leave gap, rotational parts and shell to rotation with respect to have bearing or oil lubrication between the circumferential movement and housing of housing
It is limited in a relatively small fixed range also a kind of at last fixation along the component of housing axial direction in body spatial relation
Form, which kind of axial restraint mode is all to be influenceed to have certain mobile range by technique, but in the position in space
It can be that supplementary notes technical scheme understands for persons skilled in the art to put and used in description " fixation " one word
, as long as because the technical scheme and all parts that meet the segment description of present invention first are axially being unlikely to be endless
, just must gear be limited in one it is a certain amount of move to axial in the range of, described annexation could be met, this
Individual limitation be the technical scheme of the first segment description as the implicit restriction of necessary and sufficient condition, and the first segment description technical side
Case can leave relatively large axial movement space to meet idler gear from helical gear and snail when implementing for idler gear
The axial stress engaged during bar causes axial displacement and increases the technical scheme of limit slip resistance, this section of technical scheme especially emphasized
In further add to be fixed as the technical scheme of restrictive condition.
The housing of above-mentioned differential mechanism also includes the gear or spline or spiral shell for being connected with moment of torsion input part mechanics
Silk hole；The output gear A and output gear B also include the gear or flower for being connected with torque output load mechanics respectively
Key.It is intended to describe differential mechanism structure and mechanics transitive relation in itself, differential in the description of present invention above technical scheme
Device exists with the part that the mechanics attachment structure of extraneous part is not the structure that differential mechanism realizes difference effect so not having
Tough state in above-mentioned technical proposal, but it is clear that differential mechanism and all of itself not having the part one of power source when differential mechanism works
Sample need with the external world mechanics be connected, when differential mechanism proposed by the present invention is applied to equipment the input of the moment of torsion of differential mechanism can be
Hull outside is provided with the gear circumferentially fixed with housing, and gear is engaged with torque input gear, or housing passes through spline
It is connected with input shaft and coaxial synchronous rotation；The output of moment of torsion can be distinguished from output gear A and output gear B by spline
It is connected with two output shafts and coaxial synchronous rotation, it is also possible to turned round with outside from being set on output gear A and output gear B
The square gear that is meshed of load realizes output.
Differential mechanism of the invention can realize moment of torsion by setting the gear ratio of A types idler gear and Type B idler gear
The distribution of output is set；Can also be by the gear ratio of wobble gear A and output gear A and wobble gear B and output gear B teeth
The distribution that the difference of ratio is taken turns to realize torque output is set, and this is an important advance advantage of difference device of the invention, is passed through
The gear ratio that output torque distribution is can adjust at above-mentioned two is set, various differential mechanism regulation moment of torsion distribution in the prior art are solved
It is range-restricted, also reduce compared to existing technology the difficulty of processing of moulding that differential mechanism design for regulation moment of torsion distribution with
Processing cost, the torque carrying capability under same size is more improve compared to some differential mechanisms of prior art.
The engine power that differential mechanism of the invention is mainly used in vehicle is exported by the backward wheel of gearbox, in
During the differential mechanism of centre, gearbox outputs torque to differential casing, and output gear A and output gear B output torque to respectively
Front and rear differential mechanism, during as front differential mechanism or rear differential mechanism, the moment of torsion of center differential output is exported by rotating shaft or gear and arrived
Differential casing, the output gear A and output gear B of differential mechanism output torque to left and right wheelses respectively.
The load mentioned in technical solution of the present invention is mechanical load, the part of drive is needed when referring to rotation or because needing band
The resistance that dynamic other parts rotation is produced, when automobile is applied to, load refers to just that differential mechanism needs to drive rotation axletree and car
Wheel, and the resistance that drive vehicle wheel rotation bears；Moment of torsion is also referred to as torque, the technology of the present invention when rotational parts are transmitted and rotated sometimes
Scheme description in use or be logic or relationship description.
Brief description of the drawings
The differential design schematic diagram of Fig. 1 embodiments 1（Sectional view）.
The differential mechanism part explosive view of Fig. 2 embodiments 1.
The differential mechanism stereogram of Fig. 3 embodiments 1.
The differential design schematic diagram of Fig. 4 embodiments 2（Sectional view, hides screw in figure）.
The differential mechanism idler gear close up view of Fig. 5 embodiments 2（Other parts are hidden in figure）.
The differential design schematic diagram of Fig. 6 embodiments 3（Sectional view）.
The differential design schematic diagram of Fig. 7 embodiments 4（Sectional view）.
The differential mechanism idler gear close up view of Fig. 8 embodiments 4（Other parts member-retaining portion housing is hidden in figure）.
In figure：1, housing；2, A type idler gears；3, Type B idler gear；4, wobble gear A；5, wobble gear B；6, it is defeated
Go out gear A；7, output gear B.
Specific embodiment
Embodiment 1, as shown in Fig. 1 ~ Fig. 3, the A types idler gear selected in the present embodiment is that 3 identical involutes are straight
Gear, Type B idler gear is also the number of teeth all phases of 3 identical involute spur gears, A types idler gear and Type B idler gear
Deng, 3 A types idler gears and with 3 Type B idler gears intermeshing 3 gear pairs of composition, wobble gear A and output gear A
Selected a pair of teeth difference for 2 cycloid internal gear pair, wherein output gear A is external gear, and A type idler gears two ends are machined with axle
And at one end on be machined with axially extended eccentric shaft, the eccentric shaft on 3 A type idler gears inserts wobble gear A ends respectively
Axis hole on face, wobble gear B and output gear B select a pair with wobble gear A and output gear A tooth forms and the complete phase of the number of teeth
Same cycloid internal gear pair, wherein output gear B is external gear, and Type B idler gear two ends are machined with axle and at one end upper processing
There is axially extended eccentric shaft, the eccentric shaft on 3 Type B idler gears inserts the axis hole on wobble gear B end faces respectively, export
The center of gear A and output gear B is provided with the axis hole with spline, and housing has selected one to be made up of 4 parts as shown in the figure
Component simultaneously assembles fixation with screw, and the axis hole of connection idler gear two end axles is machined with housing, is additionally provided with for pacifying on housing
Fill the mounting hole of external gear.
Embodiment 2, as shown in Figure 4 and Figure 5, the A types idler gear selected in the present embodiment is that 3 identical involutes are straight
Gear, Type B idler gear is also the number of teeth all phases of 3 identical involute spur gears, A types idler gear and Type B idler gear
Deng, each A types idler gear and adjacent two Type B idler gears intermeshing, each Type B idler gear with adjacent two
A types idler gear is intermeshed, and 6 idler gears constitute one group, so can preferably improve the torque capacity of gear,
Also the engaging friction area increase rotary resistance of idler gear is increased, wobble gear A and output gear A has selected a pair of tooth differences to be
2 cycloid internal gear pair, wherein output gear A be internal gear, A type idler gears two ends be machined with axle and at one end on be machined with
Axially extended eccentric shaft, the eccentric shaft on 3 A type idler gears inserts the axis hole on wobble gear A end faces respectively, swings tooth
Wheel B and output gear B selects a pair and wobble gear A and output gear A tooth forms and the identical cycloid internal gear pair of the number of teeth,
Wherein output gear B be internal gear, Type B idler gear two ends be machined with axle and at one end on be machined with axially extended bias
Axle, the eccentric shaft on 3 Type B idler gears inserts the axis hole on wobble gear B end faces, output gear A and output gear B respectively
On be machined with the axis hole with spline, housing has been selected a component being made up of 4 parts and has been assembled with screw solid as shown in the figure
It is fixed, the axis hole of connection idler gear two end axles is machined with housing, the mounting hole for installing external gear is additionally provided with housing.
Embodiment 3, as shown in fig. 6, the A types idler gear selected in the present embodiment is 3 identical involute spur gears,
Type B idler gear is also 3 identical involute spur gears, and the number of teeth of A types idler gear and Type B idler gear is all equal, 3
A types idler gear and with 3 Type B idler gears intermeshing 3 gear pairs of composition, wobble gear A and output gear A are selected
A pair of teeth difference for 2 cycloid internal gear pair, wherein output gear A is external gear, and A type idler gears two ends are machined with axle and one
Axially extended eccentric shaft is machined with end, the eccentric shaft on 3 A type idler gears is inserted on wobble gear A end faces respectively
Axis hole, wobble gear B and output gear B are from a pair and wobble gear A and output gear A tooth forms and the identical pendulum of the number of teeth
Line internal gear pair, wherein output gear B be external gear, Type B idler gear two ends be machined with axle and at one end on be machined with axial direction
The eccentric shaft for stretching out, the eccentric shaft on 3 Type B idler gears inserts the axis hole on wobble gear B end faces, output gear A respectively
The axis hole with spline is provided with the center of output gear B, housing has selected a component being made up of 4 parts simultaneously as shown in the figure
Assembled with screw and fixed, the axis hole of connection idler gear two end axles is machined with housing, casing center is also machined with coaxial spline
Hole is used to connect input torque by axle.
Embodiment 4, as shown in Figure 7 and Figure 8, the A types idler gear selected in the present embodiment is that 3 identical involutes are straight
Gear, Type B idler gear is also the number of teeth all phases of 3 identical involute spur gears, A types idler gear and Type B idler gear
Deng, 3 A types idler gears and with 3 Type B idler gears intermeshing 3 gear pairs of composition, three gear pairs are embedded in housing
Three breach corresponding with gear pair outline in, wobble gear A and output gear A selected a pair of teeth difference for 2 pendulum
Line internal gear pair, wherein output gear A are external gear, and axially extended eccentric shaft, 3 A are machined with A type idler gears one end
Eccentric shaft on type idler gear inserts the axis hole on wobble gear A end faces respectively, and wobble gear B and output gear B select one
Pair with wobble gear A and output gear A tooth forms and the identical cycloid internal gear pair of the number of teeth, wherein output gear B be external tooth
Wheel, is machined with axially extended eccentric shaft on Type B idler gear one end, the eccentric shaft on 3 Type B idler gears inserts pendulum respectively
The center of the axis hole on moving gear B end faces, output gear A and output gear B is provided with the axis hole with spline, and housing is selected as shown in the figure
Fixation is assembled with a component being made up of 3 parts and with screw, the peace for installing external gear is additionally provided with housing
Dress hole.
Embodiment 5, this implementation considers that be responsible for moment of torsion as center differential when differential mechanism arrives preceding with inequality proportion output
During rear axle, the unequal distribution of moment of torsion, the A type center tooths selected in example are realized by selecting different cycloid tooth wheel set tooth differences
It is 3 identical involute spur gears to take turns, and Type B idler gear is also 3 identical involute spur gears, A types idler gear and B
The number of teeth of type idler gear is all equal, 3 A types idler gears and with 3 Type B idler gears intermeshing 3 gear pairs of composition,
Wobble gear A and output gear A selected a pair of teeth difference for 2 cycloid internal gear pair, wherein output gear A is external gear, A types
Idler gear two ends be machined with axle and at one end on be machined with axially extended eccentric shaft, the eccentric shaft on 3 A type idler gears
Axis hole on insertion wobble gear A end faces respectively, wobble gear B and output gear B selected a pair of teeth difference for 3 cycloid internal tooth
Wheel set, wherein output gear B be external gear, Type B idler gear two ends be machined with axle and at one end on be machined with it is axially extended
Eccentric shaft, the eccentric shaft on 3 Type B idler gears inserts the axis hole on wobble gear B end faces, output gear A and output respectively
The center of gear B is provided with the axis hole with spline, and housing has been selected a component being made up of 4 parts and assembled with screw solid
It is fixed, it is machined with the axis hole of connection idler gear two end axles on housing, casing center is also machined with coaxial splined hole for by axle
(the unique difference basically identical with embodiment 3 of the differential design of the present embodiment is in wobble gear B and output gear for connection input torque
3) tooth difference between wheel B is set to.
Claims (10)
1. a kind of differential mechanism, it is characterized in that：Internal gear pair, the wobble gear B being made up of housing, wobble gear A and output gear A
Internal gear pair, at least two A types idler gears, at least two Type B idler gears composition constituted with output gear B；Each A type
The radial direction of idler gear is fixed and rotation axis and housing rotation diameter parallel with housing, each A types idler gear at least with
One Type B idler gear engagement, and each is identical with the gear pair gear ratio that Type B idler gear is constituted by A types idler gear, often
Individual A types idler gear is provided with the eccentric shaft of axis and its rotation diameter parallel, and the eccentric shaft on each A type idler gear is relative
Apart from identical, the eccentric shaft phase on all A types idler gears is identical, the bias on each A type idler gear for the gear axis of rotation
Axial and radial is fixed with wobble gear A respectively, and output gear A is coaxial with housing rotation rotating shaft；The radial direction of each Type B idler gear with
Housing is fixed and rotation axis and housing rotation diameter parallel, and each Type B idler gear is at least nibbled with an A type idler gear
Close, each Type B idler gear is provided with the eccentric shaft of axis and its rotation diameter parallel, the bias on each Type B idler gear
, with respect to its axis of rotation apart from identical, the eccentric shaft phase on all Type B idler gears is identical, on each Type B idler gear for axle
Eccentric shaft radial is fixed with wobble gear B respectively, and output gear B is coaxial with housing rotation rotating shaft.
2. a kind of differential mechanism according to claim 1, it is characterized in that：The housing is driven in each A type by external force rotation
Between gear and each Type B idler gear revolved round the sun around the housing axis of rotation with housing, the eccentric shaft on each A type idler gear drives
With housing into rotation, wobble gear A drives output gear A to rotate to wobble gear A, and the eccentric shaft on each Type B idler gear drives
With housing into rotation, wobble gear B drives output gear B to rotate to wobble gear B, and output gear A and output gear B is exported turn respectively
It is dynamic；When output gear A is identical with output gear B rotating speeds, all parts are motionless with respect to housing stationary in differential mechanism；Work as output gear
Wheel A is different with the output loading of output gear B when causing rotating speed different, and output gear A and output gear B relatively rotate,
Both with housing there is relative rotation in opposite direction in output gear A and output gear B respectively, causes wobble gear A and swings tooth
Wheel B all with housing occur relative to housing rotation axis revolution in opposite direction, wobble gear A and wobble gear B relative to
The revolution of housing rotation axis by eccentric shaft drive each A types idler gear and each Type B idler gear round about from
Turn, be limited to the engagement of A types idler gear and Type B idler gear, output gear A and output gear B can only be fixed with one
There is in opposite direction rotating against relative to housing in rotating ratio relation.
3. a kind of differential mechanism according to claim 1, it is characterized in that：The tooth of the wobble gear A and output gear A compositions
The gear pair of wheel set or wobble gear B and output gear B compositions is cycloid tooth wheel set.
4. a kind of differential mechanism according to claim 1, it is characterized in that：The differential mechanism includes at least 3 A type idler gears
At least 3 Type B idler gears.
5. a kind of differential mechanism according to claim 1, it is characterized in that：The output gear A and output gear B is external tooth tooth
Wheel.
6. a kind of differential mechanism according to claim 1, it is characterized in that：The output gear A and output gear B is internal tooth tooth
Wheel.
7. a kind of differential mechanism according to claim 1, it is characterized in that：The A types idler gear and Type B idler gear are
Helical gear or worm screw.
8. a kind of differential mechanism according to claim 1, it is characterized in that：The output gear A, output gear B, wobble gear
A and wobble gear B are respectively relative to housing axial restraint.
9. a kind of differential mechanism according to claim 1, it is characterized in that：Described A types idler gear and Type B intermediate gear shaft
Fixed to relative to housing.
10. a kind of differential mechanism according to claim 1, it is characterized in that：The housing of the differential mechanism also include for
The gear or spline or screw hole of moment of torsion input part mechanics connection；The output gear A and output gear B also include respectively
For the gear or spline that are connected with torque output load mechanics.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710215093.3A CN106801736B (en) | 2017-04-02 | 2017-04-02 | Differential mechanism |
| PCT/CN2018/081481 WO2018184506A1 (en) | 2017-04-02 | 2018-03-31 | Differential and cycloidal differential |
| US16/496,891 US10920865B2 (en) | 2017-04-02 | 2018-03-31 | Differential and cycloidal differential |
| EP18781709.3A EP3608558B1 (en) | 2017-04-02 | 2018-03-31 | Cycloidal differential |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710215093.3A CN106801736B (en) | 2017-04-02 | 2017-04-02 | Differential mechanism |
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| Publication Number | Publication Date |
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| CN106801736A true CN106801736A (en) | 2017-06-06 |
| CN106801736B CN106801736B (en) | 2023-01-10 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201710215093.3A Active CN106801736B (en) | 2017-04-02 | 2017-04-02 | Differential mechanism |
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| CN (1) | CN106801736B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2018184506A1 (en) * | 2017-04-02 | 2018-10-11 | 凌子龙 | Differential and cycloidal differential |
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| CN101900194A (en) * | 2010-08-27 | 2010-12-01 | 魏家斌 | Differential |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN106801736B (en) | 2023-01-10 |
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